Cam follower assembly for can bodymaker and can bodymaker including same

ABSTRACT

A cam follower assembly for a can bodymaker includes a slider structured to be coupled to the proximal end of a ram body of the can bodymaker; and a plurality of cam follower members rotatably coupled to the slider. The cam follower members are structured to be operatively coupled to a cam of a ram drive assembly.

CROSS REFERENCE TO RELATED APPLICATIONS

This application is a continuation patent application of and claimspriority to U.S. patent application Ser. No. 16/885,589, filed May 28,2020.

FIELD OF THE INVENTION

The disclosed and claimed concept relates to a can bodymaker and, morespecifically, to a cam follower assembly for use in a can bodymakerdriven by a cam.

BACKGROUND OF THE INVENTION

Generally, an aluminum can begins as a disk of aluminum, also known as a“blank,” that is punched from a sheet or coil of aluminum. That is, thesheet is fed into a press where a “blank” disk is cut from the sheet byan outer slide/ram motion. An inner slide/ram then pushes the “blank”through a draw process to create a cup. The cup has a bottom and adepending sidewall. The cup is fed into a bodymaker which furtherperforms a redraw and ironing operation that forms the cup into a canbody. That is, the bodymaker includes a punch disposed on an elongated,reciprocating ram assembly. The cup is positioned in front of the punchwhich then moves the cup through a die pack wherein the radius of thecup is reduced and the depending sidewall is elongated and thinned.

More specifically, the cup is disposed at the mouth of a die pack havingmultiple dies defining passages. The cup is held in place by a redrawsleeve, which is part of a redraw assembly. As the punch/ram engages thecup, the cup is moved through a passage in a redraw die. The cup is thenmoved through a number of ironing dies. That is, the ironing dies aredisposed behind, and axially aligned with, the redraw die. At the end ofthe die pack opposite the ram is a domer. The domer is a die structuredto form a concave dome in the bottom of the cup/can body.

Generally, and as shown in FIG. 1 , a bodymaker 1 includes a driveassembly 2 and a forming assembly 3. The drive assembly 2 includes amotor (not shown) that is operatively coupled to a rotating crank 4having a flywheel (not numbered) coupled thereto of considerable massfor storing kinetic energy for metal forming such that the motor doesnot have to supply variable energy. The crank 4 is further coupled to apivoting swing arm 5 by a first connecting rod 6A. The swing arm 5 iscoupled, via a second connecting rod 6B, to a ram assembly 7. That is,the forming assembly 3 includes the ram assembly 7, a die pack 8 and adomer 9. The ram assembly 7 includes a carriage 7A and an elongated ram(or ram body) 7B and, in some embodiments, a punch 7C disposed at thedistal end of the ram body 7B from the second connecting rod 6B. The diepack 8 includes a number of ironing dies (not numbered) which define aforming passage (not numbered). The ram body 7B/punch 7C is structuredto, and does, reciprocate through the die pack 8. That is, the ram body7B/punch 7C moves between a first position, wherein the ram body7B/punch 7C is withdrawn from the die pack 8 (i.e., shifted to the rightin FIG. 1 ), and a second position, wherein the ram body 7B/punch 7Cextends through the die pack 8 to a position adjacent the domer 9 (i.e.,shifted to the left in FIG. 1 ). As is known, a cup feeder, notnumbered, positions a cup at the mouth, or upstream end, of the die pack8 when the ram body 7B is in the first position. Thus, as the ram body7B moves toward the second position, the ram body 7B/punch 7C moves thecup through the die pack 8 where it is formed into a can body. The useof a crank, a swing arm, and/or pivoting connecting rods in a bodymakerdrive assembly is a problem. That is, there are many disadvantagesassociated with a crank/swing arm drive assembly in a bodymaker asdiscussed below.

For example, in this configuration, the circular motion of the crank 4is converted into a reciprocal motion in the ram body 7B and punch 7C.The crank 4 rotates at speeds of about 320 r.p.m. to 400 r.p.m. and theram body 7B/punch 7C reciprocates once during each cycle. A can body isformed during each cycle; thus, the bodymaker 1 makes about 320 to 400cans per minute. That is, for each cycle of the drive assembly 2, i.e.,each time the crank 4 rotates three hundred and sixty degrees (360°),the bodymaker 1 makes one can body. Alternatively, in an embodimentwherein the crank 4 drives two ram bodies 7B, the bodymaker 1 makes twocan bodies during each cycle. As it is desirable to produce as many canbodies per minute as possible, the number of can bodies made per cycleis a problem. That is, it is desirable to have a bodymaker operatingwith a higher, or greater, output.

Operating at a higher speed, however, is difficult due to thelimitations and characteristics of the elements of the bodymaker. Forexample, the ram and punch are made of metal, typically steel, and havea considerable mass. The drive assembly must be structured to move themass of the ram and punch and to resist the forces generated by themoving ram and punch. Thus, as discussed above, the drive assembly isalso, typically, made of metal/steel and, as such, also has aconsiderable mass. Further, the elements of the drive assembly aresubstantially rigid and coupled to each other at rotational and pivotalcouplings. At this speed, and in this configuration, there are a numberof detrimental effects on elements of the bodymaker drive assembly 2.That is, this configuration includes rigid, elongated elements (whichinclude the swing arm 5, connecting rods 6A, 6B and ram body 7B) whichare operatively engaged by a rotating element (i.e., the crank 4 andflywheel). As the rotational motion of the crank 4 is converted into thereciprocating motion of the ram body 7B, the rigid elements move and areeither accelerating or decelerating (except for the instant whereinacceleration becomes deceleration). That is, the drive assembly andcertain forming assembly elements are, essentially, either acceleratingor decelerating and are, essentially, never moving at a constantvelocity. This type of motion, i.e., not moving at a constant velocity,causes the distal end of the ram body, including the punch, to vibrate.This is a problem.

Further, a bodymaker in a drive assembly configured as described above,i.e., a crank operatively coupled to a swing arm that is furtheroperatively coupled to a ram assembly, all of the elements are,essentially, in constant motion. That is, with the exception of theinstant when the ram assembly reverses direction, the elementsoperatively coupled to the drive assembly are in constant motion. Abodymaker in this configuration has problems.

For example, the motion of the elongated elements of the drive assemblyand/or the ram assembly is suddenly, or instantly, reversed from aforward motion to a rearward motion. This rapid change in the directionof the motion is, as used herein, “whiplash.” At the forward end of theram body 7B stroke, this effect causes an undesirable vibration in theram body 78 which is transferred to the die pack 8. At the rearward endof the ram body 7B stroke, the rapid change in direction causes anundesirable vibration just before the punch 7C engages a cup. Further,at these speeds and with such rapid changes in the motion, the momentumof the various elements and the interaction between elements cause theelongated elements of the drive assembly to deform/elongate. Thiselongation, in turn, causes the position of the ram assembly 7 relativeto the die pack 8 and domer 9 to change. More specifically, the distalend of the ram/punch will, essentially, be positioned beyond the domer.This condition is identified herein as “overstroke.” That is, as usedherein, the “overstroke” of the ram/punch means that when the ram is inthe second position, the elongation of the ram (and/or other elements)position the distal end of the ram/punch further than is necessary toform the dome in the cup; i.e., the distal end of the ram/punch ispositioned too close to the domer, which can damage the ram/punch,domer, and/or result in improperly formed can bodies. To prevent suchoverstroke and damage resulting therefrom, the positioning of formingarrangements of such prior art arrangements are typically adjusted forthe maximum production speed, and thus positioned for the maximumdeformations and not properly positioned for operation at lower speeds(and thus lower deformations). Accordingly, in order to avoid potentialdamage and/or improperly formed can bodies at less than maximumproduction speeds the flywheels of such arrangements have to be engagedto the forming ram motion mechanisms in no more than two strokes withoutmaking cans at speeds no less than 80% of the maximum speed required.Such engagement is rather abrupt and requires a strong clutch. These areproblems.

It is noted that certain forming devices used in the process of makingcans and/or can bodies, utilize a cam in the drive assembly. Forexample, “necker” machines, i.e., machines structured to form necks incan bodies, often utilize a fixed cam disk and rotating formingassemblies. That is, the cam disk is fixed to a housing or othermounting and a plurality of forming assemblies move about the cam. Asthe forming assemblies move, the forming assemblies engage the cam andthe cam drives dies and other forming elements within the formingassemblies. Thus, the cam is static and the forming assemblies aredynamically mounted. That is, the entire forming assembly moves whilethe internal elements of the forming assemblies move relative to eachother. Generally, the mounting assemblies for the forming assemblies arecomplex and are subject to wear and tear. This is a problem. That is,having a static cam and dynamically mounted forming assemblies is aproblem.

Further, the drive assembly linkage of FIG. 1 as described aboveincludes at least three rotational couplings that undergo a pivotingmotion (connecting rod 6A/swing arm 5, swing arm 5/connecting rod 6B andconnecting rod 6B/carriage 7A). These rotational couplings arehereinafter, and as used herein, identified as “pivotal” couplings. Whenmaintenance is required, or when the drive assembly and the formingassembly are being swapped with another drive assembly and formingassembly to form can bodies with different characteristics, techniciansmust perform multiple decoupling/coupling operations at eachrotational/pivotal coupling. The replacement of elements joined bypivotal couplings is a time-consuming process. For example, while thedrive assembly elements are being replaced, the bodymaker is notoperational. As such, a drive assembly 2 that includes pivotal couplingsis a problem.

Stated alternately, the drive assembly 2 drive device, i.e., theconstruct that generates motion (which is the motor in the embodimentdescribed above) is operatively coupled to the ram assembly 7 via amulti-element linkage, i.e., crank 4/swing arm 5/first connecting rod6A/second connecting rod 6B. Such a multi-element linkage cannot act asa “direct operative coupling element” between the motor and the ramassembly. This is a problem because as the number of elements increase,the cost, the weight of the drive assembly, and the energy required tooperate the drive assembly increase.

Further, when the separate elements of the forming assembly are beinginstalled, the elements must be carefully aligned with each other. Forexample, the ram must be aligned with the forming passage through thedie pack and with the domer. As there are multiple elements in theforming assembly that are completely separate from each other, thisprocess takes a considerable amount of time during which the bodymakeris not operational. This is a problem. That is, a forming assemblywherein the moving elements are not maintained in alignment with thestationary elements of the forming assembly is a problem.

It is understood that, as the speed of the drive assembly increases,these problems are intensified. Thus, there is a limit as to how manycan bodies a bodymaker having such a drive assembly is able to form. Oneadaptation that allows for additional can bodies to be formed includes asecond forming assembly. The second forming assembly includes a ramassembly that moves in opposition to the first forming assembly ramassembly. That is, generally, the crank is operatively coupled to twoseparate rams. When the first ram assembly is in the first position, thesecond ram assembly is in the second position, and, when the first ramassembly is in the second position, the second ram assembly is in thefirst position. Thus, the rams are generally moving in opposition toeach other. This configuration effectively doubles the output of thebodymaker. The problem with this configuration is that when one ramassembly needs to be replaced or repaired, both ram assemblies arenon-operational. That is, due to balance and similar issues, it is notpossible to operate the bodymaker with less than all formingassemblies/ram assemblies coupled to the drive assembly. This is aproblem.

Further, in such a bodymaker with two rams generally moving inopposition to each other, certain actions occur simultaneously, or nearsimultaneously, such as the reversal in the direction the ram is moving.Thus, both rams experience “whiplash” at the same time. This is aproblem because such simultaneous actions generate an undesirablevibration and, moreover, this vibration is more intense than in abodymaker with a single ram. That is, it is not desirable to havevibration generating actions occur at the same time to different rambodies. This is a problem.

Further, when the elements of the drive assembly and/or ram assembly arein constant motion, the length of the ram stroke, i.e., the distancebetween the first and second positions, must be larger. That is, asdescribed above, prior to being formed in the die pack, a cup must bepositioned in front of the ram/punch at the die pack. Generally, a cupfeeder, or similar device, is structured to start moving a cup intoposition, i.e., at the mouth of the die pack, as soon as the ram haswithdrawn from the die pack. As the ram is in constant motion, the rammust be moving the entire time the cup is being positioned. That is, theram cannot stop once it is retracted from the die pack. Thus, the ramstroke length must have a sufficient length so that there is enough timefor a cup to be placed at the mouth of the die pack prior to the rammoving forward to engage the cup and move the cup through the die pack.Thus, the stroke length is a problem.

For a 12-ounce standard beverage can body, the ram assembly travels overa distance of nineteen inches to twenty-four inches or sometimes more.That is, for example, the distal end of the ram body 7B moves a distanceof nineteen inches to twenty-four inches or more as the ram body 7Bmoves from the retracted, first position to the extended, secondposition; the distance the ram moves is, as used herein, the “strokelength.” The longer the stroke length, the larger/longer the elements ofthe drive assembly must be. Larger/longer elements require more energyto move. This is a problem. Smaller/shorter elements are desirable. Thatis, smaller/shorter elements generate a shorter stroke length and have areduced weight. Elements that have a reduced weight require less energyto operate. Thus, a bodymaker with a shorter stroke length is desirableand would solve these problems.

There is, therefore, a need for a bodymaker drive assembly that does notinclude either a crank, a swing arm, and/or pivoting connecting rods.There is a further need for a bodymaker that is structured to produceone of a large number of can bodies per minute, a very large number ofcan bodies per minute, or an exceedingly large number of can bodies perminute. There is a further need for a bodymaker drive assembly whereinthe drive assembly imparts a motion to the forming assembly wherein atleast some of the motion is at a constant velocity. There is a furtherneed for a bodymaker drive assembly that does not create a sudden, orinstant, change in the direction of the movable forming assemblyelements, i.e., a bodymaker drive assembly that is structured to causethe movable forming assembly elements to dwell prior to changingdirections. There is a further need for a bodymaker drive assembly thatdoes not include pivotal couplings. There is a further need for abodymaker with a unified forming assembly. There is a further need for abodymaker having a plurality of forming assemblies wherein, if less thanall of the forming assemblies are engaged, the bodymaker is stilloperational. There is a further need for a bodymaker drive assemblyhaving a reduced stroke length.

Another manner of increasing the output of the bodymaker is to includemultiple rams that are driven by a single drive assembly. That is,certain bodymakers include multiple drive assemblies wherein each driveassembly is associated with an independent ram. These are, essentially,independent bodymakers that have separate drive assemblies linkedtogether. This is done so that the timing of the coupled bodymakers canbe controlled. Bodymakers in this configuration do not include multiplerams that are driven by a single drive assembly. Other bodymakers,however, have a single drive assembly that is structured to, and does,drive multiple rams.

For example, U.S. Pat. No. 9,162,274 discloses a double-action bodymakerhaving a single motor that is coupled to a crank having offset journalswhich are further coupled to two separate rams. The two rams move inopposition, and in opposite directions, relative to each other. Morespecifically, when compared to the bodymaker described above, thedouble-action bodymaker includes a single motor, a single crank (withtwo journals), two swing levers and two rams. The rams extend ingenerally opposite directions and move in opposition to each other. Thatis, when one ram is in the first position, the second ram is in thesecond position. Moreover, a bodymaker in this configuration includestwo pivoting elements, i.e., the swing levers.

As an alternate example, U.S. Pat. No. 10,343,208 discloses a verticalbodymaker having a single motor that is coupled, via a single crank withoffset journals, to two separate ram assemblies. The rams move inopposition, but in the same direction, relative to each other. Morespecifically, when compared to the bodymaker described above, thevertical bodymaker includes a single motor, a single crank (with twojournals), two connecting rods and two ram assemblies. U.S. Pat. No.10,343,208 notes that the bodymaker, in an embodiment that is not shown,includes more than two ram assemblies. In this configuration there wouldbe, for example, two synchronized ram assemblies moving toward thesecond position at the same time, and two synchronized ram assembliesmoving toward the first position at the same time. That is, the pairs ofram assemblies move in opposition to each other.

As another alternate example, U.S. Pat. No. 7,882,721 discloses abodymaker having a single motor coupled to a gearbox having a crank armthat is operatively coupled to two ram assemblies. In thisconfiguration, the two rams move in opposition, and in oppositedirections, relative to each other.

The swing levers in U.S. Pat. No. 9,162,274 and the connecting rods inU.S. Pat. No. 10,343,208 are substantially similar to the “swing arm 5”of FIG. 1 , described above. That is, the combination of the crank andthe “swing arm 5,” and/or the similar elements noted above, are theconstructs that convert the rotational motion of the motor output shaftto a reciprocal motion in the rams. It is understood that guides andother constructs control, or limit, the path over which the ram travels,but the crank/swing arms (or similar constructs) are the elements thatconvert the rotational motion of the motor output shaft to a reciprocalmotion in the rams. Similarly, the gearbox of U.S. Pat. No. 7,882,721converts the rotational motion of the motor output shat to a reciprocalmotion in the rams. Such configurations are a problem in that the motormust drive multiple elements so as to convert the rotational motion ofthe motor output shaft to a reciprocal motion in the ram. That is, thecrank/swing arms/gearbox elements are heavy; thus, the motor must bemore robust, i.e., able to drive heavy elements. Such motors areexpensive. Further, the crank/swing arms/gearbox are prone to wear andtear. Thus, a bodymaker with multiple swing arms or a gearbox is moreexpensive to maintain. These are problems with the prior art.

Further, in such bodymakers, the drive assembly is structured, i.e.,balanced, to operate the ram assemblies at the same time. That is, forexample, if one of the two ram assemblies is not in operation, thebodymaker cannot be used with one ram assembly as the loads/reactiveloads are unbalanced which causes the drive assembly to becomeinoperable.

Further, while it is desirable to increase the output of a bodymaker, itis not desirable to increase the floor space required by the bodymaker.That is, for example, a single Standun Bodymaker (manufactured by StolleMachinery Company, LLC) arrangement, such as generally shown in FIG. 1 ,occupies about 333 square feet. Ostensibly, one could provide a singlehousing for two such bodymakers and assert that the output has doubled.But it is understood that the floor space required by such a bodymakerwould be about double the floor space required by one such bodymaker.This is a problem. That is, increasing the output of a bodymaker whilelimiting the floor space required by one such bodymaker is a problem.

There is, therefore, a need for a bodymaker with a direct ram driveassembly, i.e., a ram drive assembly that does not include a swing armor a gearbox. There is a further need for a bodymaker with a ram driveassembly structured to operate wherein no two ram bodies are in the samemedial position at one time and/or wherein the forming assemblies areasymmetrical forming assemblies. There is a further need for a bodymakerwith a ram drive assembly structured to operate with less than a fullset of forming assemblies. That is, there is a further need for abodymaker with a limited load ram drive. There is a further need for abodymaker structured to produce one of a large number of can bodies perminute, a very large number of can bodies per minute, or an exceedinglylarge number of can bodies per minute. There is a further need for sucha bodymaker to occupy a reduced floor space. There is a further need forsuch a bodymaker to have a single source/multiple output ram driveassembly. The bodymaker as described below and variations thereof solvethe stated problems.

SUMMARY OF THE INVENTION

These needs, and others, are met by at least one embodiment of thedisclosed concept that provides a cam follower assembly for a canbodymaker, the cam follower assembly comprising: a slider structured tobe coupled to the proximal end of a ram body of a can bodymaker; and aplurality of cam follower members rotatably coupled to the slider,wherein the cam follower members are structured to be operativelycoupled to a cam of a ram drive assembly.

The cam follower assembly may further comprise a cam follower bearingassembly having a number of hydrostatic/hydrodynamic bearing padspositioned and structured to engage with corresponding, cooperativelypositioned, bearing members.

Each bearing pad may include a recessed bearing pocket that isstructured to generally house a pressurized supply of bearing fluidprovided therein.

The slider may comprise a slider body and an upper frame portionextending upward from the slider body, and the number ofhydrostatic/hydrodynamic bearing pads may be provided on the upper frameportion.

The upper frame portion of the slider body may comprise: a first memberextending upward generally from at or near a first edge of the sliderbody; a second member extending upward generally from at or near asecond edge of the slider body; and a third member extending between thefirst and second members and spaced a distance above the slider body.

The number of hydrostatic/hydrodynamic bearing pads may include: a firstbearing pad coupled to an outward facing face of the first member; asecond bearing pad coupled to an outward facing face of the secondmember; and a third bearing pad coupled to an upward facing face of thethird member.

The slider may further comprise a lower frame portion extending downwardfrom the slider body.

The lower frame portion may comprise: a first member extending downwardgenerally from at or near a first edge of the slider body; a secondmember extending downward generally from at or near a second edge ofslider body opposite the first edge; and a third member extendingbetween the first and second members and spaced a distance below theslider body.

Each of the cam followers may comprise a roller bearing.

One of the roller bearings may include an eccentric bushing positionablebetween a first positioning, wherein the one roller bearing is disposeda first distance from another one of the plurality of roller bearings,and a second positioning, wherein the one roller bearing is disposed asecond distance, different than the first distance, from the other oneof the plurality of roller bearings.

As another embodiment of the disclosed concept, a moving assembly for acan bodymaker comprises: a ram assembly including an elongated ram bodyhaving a proximal end and an opposite distal end; and a cam followerassembly such as previously described.

As yet a further embodiment of the disclosed concept, a can bodymakercomprises: a ram drive assembly including one of a disk cam or a barrelcam; and a moving assembly such as previously described.

BRIEF DESCRIPTION OF THE DRAWINGS

A full understanding of the disclosed concept can be gained from thefollowing description of the preferred embodiments when read inconjunction with the accompanying drawings in which:

FIG. 1 is a schematic side elevation view of a prior art bodymaker.

FIG. 2 is a schematic top view of a bodymaker with four formingassemblies driven by a disk cam in accordance with one exampleembodiment of the disclosed concept.

FIG. 3 is a schematic partially-sectional side elevation view of thebodymaker of FIG. 2 taken along the line identified in FIG. 2 .

FIG. 4 is a schematic detail cross-sectional side elevation view of aforming assembly of the bodymaker of FIGS. 2 and 3 , as indicated inFIG. 3 , shown in an operational engaged position with the disk cam.

FIG. 5 is a schematic detail cross-sectional side elevation view of acam follower of the bodymaker of FIGS. 2-4 as indicated in FIG. 4 .

FIG. 6 is a schematic detail cross-sectional side elevation view ofanother forming assembly of the bodymaker of FIGS. 2 and 3 , asindicated in FIG. 3 , shown in a non-operational disengaged positionfrom the disk cam.

FIG. 7A is a schematic top view of a ram guide assembly in accordancewith one example embodiment of the disclosed concept shown with aportion removed to show details below. FIG. 7B is a schematiccross-sectional side elevation view of the ram guide assembly of FIG. 7Aas indicated in FIG. 7A. FIG. 7C is a schematic cross-sectionalelevation view of the ram guide assembly of FIGS. 7A and 7B as indicatedin FIG. 7A. FIG. 7D is a schematic perspective view of a portion of thecam follower of the ram guide assembly of FIGS. 7A-7C.

FIG. 8A is a schematic top view of a redraw assembly in accordance withone example embodiment of the disclosed concept. FIG. 8B is a schematicsectional view of the redraw assembly of FIG. 8A as indicated in FIG.8A. FIG. 8C is a schematic sectional view of the redraw assembly ofFIGS. 8A and 8B as indicated in FIG. 8B.

FIG. 9A is a schematic top view of a redraw assembly in accordance withone example embodiment of the disclosed concept. FIG. 9B is a schematicsectional view of the redraw assembly of FIG. 9A as indicated in FIG.9A. FIG. 9C is a schematic sectional view of the redraw assembly ofFIGS. 9A and 9B as indicated in FIG. 9B.

FIG. 10 is a schematic top view of a bodymaker with two formingassemblies driven by a barrel cam in accordance with one exampleembodiment of the disclosed concept.

FIG. 11 is a schematic partially-sectional side elevation view of thebodymaker of FIG. 10 taken along the line indicated in FIG. 10 .

FIG. 12 is a schematic top view of a cam in accordance with one exampleembodiment of the disclosed concept. FIG. 12A is a graph showing thedisplacement of a punch during a stroke associated with the cam of FIG.12 . FIG. 12B is a graph showing the velocity of a punch during a strokeassociated with the cam of FIG. 12 .

FIG. 12C is a graph showing the acceleration of a punch during a strokeassociated with the cam of FIG. 12 .

FIG. 13 is a schematic top view of a bodymaker with eight formingassemblies and related machinery in accordance with one exampleembodiment of the disclosed concept.

FIG. 14 is a schematic top view of eight prior art bodymakers andrelated machinery arranged in a known manner and required spacing.

DETAILED DESCRIPTION OF THE INVENTION

It will be appreciated that the specific elements and embodimentsillustrated in the figures herein and described in the followingspecification are simply exemplary embodiments of the disclosed concept,which are provided as non-limiting examples solely for the purpose ofillustration. Therefore, specific dimensions, orientations, assembly,number of components used, embodiment configurations and other physicalcharacteristics related to the embodiments disclosed herein are not tobe considered limiting on the scope of the disclosed concept.

Directional phrases used herein, such as, for example, clockwise,counterclockwise, left, right, top, bottom, upwards, downwards andderivatives thereof, relate to the orientation of the elements shown inthe drawings and are not limiting upon the claims unless expresslyrecited therein.

As used herein, the singular form of“a,” “an,” and “the” include pluralreferences unless the context clearly dictates otherwise.

As used herein, “movably coupled” means that two elements are coupled ina manner such that at least some movement of one or both of the elementswith respect to the other element is permitted without uncoupling theelements. For example, a door is “movably coupled” to a door frame byone or more hinges.

As used herein, “selectively coupled” means that two or more elementsare coupled in a manner which may be readily undone without causingdamage to either of such elements. For example, two elements that arebolted or screwed together are “selectively coupled”, while two elementsthat are glued or welded together are not “selectively coupled” as usedherein.

As used herein, “structured to [verb]” means that the identified elementor assembly has a structure that is shaped, sized, disposed, coupledand/or configured to perform the identified verb. For example, a memberthat is “structured to move” is movably coupled to another element andincludes elements that cause the member to move or the member isotherwise configured to move in response to other elements orassemblies. As such, as used herein, “structured to [verb]” recitesstructure and not function. Further, as used herein, “structured to[verb]” means that the identified element or assembly is intended to,and is designed to, perform the identified verb. Thus, an element thatis merely capable of performing the identified verb but which is notintended to, and is not designed to, perform the identified verb is not“structured to [verb].”

As used herein, in a term such as, but not limited to, “[X] structuredto [verb][Y],” the “[Y]” is not a recited element. Rather, “[Y]” furtherdefines the structure of “[X].” That is, assume in the following twoexamples “[X]” is “a mounting” and the [verb] is “support.” In a firstexample, the full term is “a mounting structured to support a flyingbird.” That is, in this example, “[Y]” is “a flying bird.” It is knownthat flying birds, as opposed to swimming birds or walking birds,typically grasp a branch for support. Thus, for a mounting, i.e., “[X],”to be “structured” to support a bird, the mounting is shaped and sizedto be something a bird is able to grasp similar to a branch. This doesnot mean, however, that the bird is a recited element. In a secondexample, “[Y]” is a house; that is the second exemplary term is “amounting structured to support a house.” In this example, the mountingis structured as a foundation as it is well known that houses aresupported by foundations. As before, the house is not a recited element,but rather defines the shape, size, and configuration of the mounting,i.e., the shape, size, and configuration of “[X]” in the term “[X]structured to [verb] [Y].”

As used herein, “associated” means that the elements are part of thesame assembly and/or operate together, or, act upon/with each other insome manner. For example, an automobile has four tires and four hubcaps.While all the elements are coupled as part of the automobile, it isunderstood that each hubcap is “associated” with a specific tire.

As used herein, a “coupling assembly” includes two or more couplings orcoupling components. The components of a coupling or coupling assemblyare generally not part of the same element or other component. As such,the components of a “coupling assembly” may not be described at the sametime in the following description.

Further, as used herein, a “cooperative coupling” or a “cooperativecoupling assembly” includes two or more couplings or couplingcomponents. The components of a cooperative coupling assembly aregenerally not part of the same element or other component. As such, thecomponents of a “cooperative coupling assembly” may not be described atthe same time in the following description. “Cooperative couplingassemblies” include, but are not limited to, (1) a combination of a nut,a bolt and passages in other elements through which the bolt extends,(2) a screw/rivet and passages in other elements through which thescrew/rivet extend, and (3) tongue-and-groove assemblies.

As used herein, a “unilateral coupling” or a “unilateral couplingassembly” means a construct that is structured to be coupled to anotherelement or assembly wherein the other element or assembly is notstructured to be coupled to the “unilateral coupling.” “Unilateralcoupling assemblies” include, but are not limited to clamps, tensionmembers (e.g., a rope), and adhesive constructs. Further, it isunderstood that the nature of such constructs as a “unilateral couplingassembly” depend upon the other element to which the coupling assemblyis coupled. That is, for example, reins on a horse are a “unilateralcoupling” when coupled to a tree because the tree is not a constructthat is structured to be coupled to the reins. Conversely, reins on ahorse are a “cooperative coupling” when coupled to a hitching postbecause a hitching post is a construct that is structured to be coupledto the reins.

As used herein, a “coupling” or “coupling component(s)” is one or morecomponent(s) of a “coupling assembly,” i.e., either a “cooperativecoupling” or a “unilateral coupling.” That is, a cooperative couplingassembly includes at least two components that are structured to becoupled together. It is understood that the components of a cooperativecoupling assembly are compatible with each other. For example, in acooperative coupling assembly, if one coupling component is a snapsocket, the other cooperative coupling component is a snap plug, or, ifone cooperative coupling component is a bolt, then the other cooperativecoupling component is a nut (as well as an opening through which thebolt extends) or threaded bore. In a “unilateral coupling,” the“coupling” or “coupling component” is the construct that is structuredto be coupled to another construct. For example, given a rope with aloop formed thereon, the loop in the rope is the “coupling” or “couplingcomponent.”

As used herein, a “fastener” is a separate component structured tocouple two or more elements. Thus, for example, a bolt is a “fastener”but a tongue-and-groove coupling is not a “fastener.” That is, thetongue-and-groove elements are part of the elements being coupled andare not a separate component.

As used herein, the statement that two or more parts or components are“coupled” shall mean that the parts are joined or operate togethereither directly or indirectly, i.e., through one or more intermediateparts or components, so long as a link occurs. As used herein, “directlycoupled” means that two elements are directly in contact with eachother. As used herein, “fixedly coupled” or “fixed” means that twocomponents are coupled so as to move as one while maintaining a constantorientation relative to each other. Accordingly, when two elements arecoupled, all portions of those elements are coupled. A description,however, of a specific portion of a first element being coupled to asecond element, e.g., an axle first end being coupled to a first wheel,means that the specific portion of the first element is disposed closerto the second element than the other portions thereof. Further, anobject resting on another object held in place only by gravity is not“coupled” to the lower object unless the upper object is otherwisemaintained substantially in place. That is, for example, a book on atable is not coupled thereto, but a book glued to a table is coupledthereto.

As used herein, the phrase “removably coupled” or “temporarily coupled”means that one component is coupled with another component in anessentially temporary manner. That is, the two components are coupled insuch a way that the joining or separation of the components is easy andwould not damage the components. For example, two components secured toeach other with a limited number of readily accessible fasteners, i.e.,fasteners that are not difficult to access, are “removably coupled”whereas two components that are welded together or joined by difficultto access fasteners are not “removably coupled.” A “difficult to accessfastener” is one that requires the removal of one or more othercomponents prior to accessing the fastener wherein the “other component”is not an access device such as, but not limited to, a door.

As used herein, “temporarily disposed” means that a first element(s) orassembly (ies) is(are) resting on a second element(s) or assembly(ies)in a manner that allows the first element/assembly to be moved withouthaving to decouple or otherwise manipulate the first element. Forexample, a book simply resting on a table, i.e., the book is not gluedor fastened to the table, is “temporarily disposed” on the table.

As used herein, “operatively coupled” means that a number of elements orassemblies, each of which is movable between a first position and asecond position, or a first configuration and a second configuration,are coupled so that as the first element moves from oneposition/configuration to the other, the second element moves betweenpositions/configurations as well. It is noted that a first element maybe “operatively coupled” to another without the opposite being true.With regard to electronic devices, a first electronic device is“operatively coupled” to a second electronic device when the firstelectronic device is structured to, and does, send a signal or currentto the second electronic device causing the second electronic device toactuate or otherwise become powered or active.

As used herein, the statement that two or more parts or components“engage” one another means that the elements exert a force or biasagainst one another either directly or through one or more intermediateelements or components. Further, as used herein with regard to movingparts, a moving part may “engage” another element during the motion fromone position to another and/or may “engage” another element once in thedescribed position. Thus, it is understood that the statements, “whenelement A moves to element A first position, element A engages elementB,” and “when element A is in element A first position, element Aengages element B” are equivalent statements and mean that element Aeither engages element B while moving to element A first position and/orelement A engages element B while in element A first position.

As used herein, “operatively engage” means “engage and move.” That is,“operatively engage” when used in relation to a first component that isstructured to move a movable or rotatable second component means thatthe first component applies a force sufficient to cause the secondcomponent to move. For example, a screwdriver may be placed into contactwith a screw. When no force is applied to the screwdriver, thescrewdriver is merely “temporarily coupled” to the screw. If an axialforce is applied to the screwdriver, the screwdriver is pressed againstthe screw and “engages” the screw. However, when a rotational force isapplied to the screwdriver, the screwdriver “operatively engages” thescrew and causes the screw to rotate. Further, with electroniccomponents, “operatively engage” means that one component controlsanother component by a control signal or current.

As used herein, in the phrase “[x] moves between its first position andsecond position,” or, “[y] is structured to move [x] between its firstposition and second position,” “[x]” is the name of an element orassembly. Further, when [x] is an element or assembly that moves betweena number of positions, the pronoun “its” means “[x],” i.e., the namedelement or assembly that precedes the pronoun “its.”

As used herein, “correspond” indicates that two structural componentsare sized and shaped to be similar to each other and may be coupled witha minimum amount of friction. Thus, an opening which “corresponds” to amember is sized slightly larger than the member so that the member maypass through the opening with a minimum amount of friction. Thisdefinition is modified if the two components are to fit “snugly”together. In that situation, the difference between the size of thecomponents is even smaller whereby the amount of friction increases. Ifthe element defining the opening and/or the component inserted into theopening is made from a deformable or compressible material, the openingmay even be slightly smaller than the component being inserted into theopening. With regard to surfaces, shapes, and lines, two, or more,“corresponding” surfaces, shapes, or lines have generally the same size,shape, and contours. With regard to elements/assemblies that are movableor configurable, “corresponding” means that when elements/assemblies arerelated and that as one element/assembly is moved/reconfigured, then theother element/assembly is also moved/reconfigured in a predeterminedmanner. For example, a lever including a central fulcrum and elongatedboard, i.e., a “see-saw” or “teeter-totter,” the board has a first endand a second end. When the board first end is in a raised position, theboard second end is in a lowered position. When the board first end ismoved to a lowered position, the board second end moves to a“corresponding” raised position. Alternately, a cam shaft in an enginehas a first lobe operatively coupled to a first piston. When the firstlobe moves to its upward position, the first piston moves to a“corresponding” upper position, and, when the first lobe moves to alower position, the first piston, moves to a “corresponding” lowerposition.

As used herein, a “path of travel” or “path,” when used in associationwith an element that moves, includes the space an element moves throughwhen in motion. As such, any element that moves inherently has a “pathof travel” or “path.” Further, a “path of travel” or “path” relates to amotion of one identifiable construct as a whole relative to anotherobject. For example, assuming a perfectly smooth road, a rotating wheel(an identifiable construct) on an automobile generally does not moverelative to the body (another object) of the automobile. That is, thewheel, as a whole, does not change its position relative to, forexample, the adjacent fender. Thus, a rotating wheel does not have a“path of travel” or “path” relative to the body of the automobile.Conversely, the air inlet valve on that wheel (an identifiableconstruct) does have a “path of travel” or “path” relative to the bodyof the automobile. That is, while the wheel rotates and is in motion,the air inlet valve, as a whole, moves relative to the body of theautomobile.

As used herein, a “planar body” or “planar member” is a generally thinelement including opposed, wide, generally parallel surfaces, i.e., theplanar surfaces of the planar member, as well as a thinner edge surfaceextending between the wide parallel surfaces. That is, as used herein,it is inherent that a “planar” element has two opposed planar surfaceswith an edge surface extending therebetween. The perimeter, andtherefore the edge surface, may include generally straight portions,e.g., as on a rectangular planar member such as on a credit card, or becurved, as on a disk such as on a coin, or have any other shape.

As used herein, the word “unitary” means a component that is created asa single piece or unit. That is, a component that includes pieces thatare created separately and then coupled together as a unit is not a“unitary” component or body.

As used herein, “unified” means that all the elements of an assembly aredisposed in a single location and/or within a single housing, frame orsimilar construct.

As used herein, the term “number” shall mean one or an integer greaterthan one (i.e., a plurality). That is, for example, the phrase “a numberof elements” means one element or a plurality of elements. It isspecifically noted that the term “a ‘number’ of [X]” includes a single[X].

As used herein, a “radial side/surface” for a circular or cylindricalbody is a side/surface that extends about, or encircles, the centerthereof or a height line passing through the center thereof. As usedherein, an “axial side/surface” for a circular or cylindrical body is aside that extends in a plane extending generally perpendicular to aheight line passing through the center. That is, generally, for acylindrical soup can, the “radial side/surface” is the generallycircular sidewall and the “axial side(s)/surface(s)” are the top andbottom of the soup can. Further, as used herein, “radially extending”means extending in a radial direction or along a radial line. That is,for example, a “radially extending” line extends from the center of thecircle or cylinder toward the radial side/surface. Further, as usedherein, “axially extending” means extending in the axial direction oralong an axial line. That is, for example, an “axially extending” lineextends from the bottom of a cylinder toward the top of the cylinder andsubstantially parallel to, or along, a central longitudinal axis of thecylinder.

As used herein, a “tension member” is a construct that has a maximumlength when exposed to tension, but is otherwise substantially flexible,such as, but not limited to, a chain or a cable.

As used herein, “generally curvilinear” includes elements havingmultiple curved portions, combinations of curved portions and planarportions, and a plurality of linear/planar portions or segments disposedat angles relative to each other thereby forming a curve.

As used herein, an “elongated” element inherently includes alongitudinal axis and/or longitudinal line extending in the direction ofthe elongation.

As used herein, “about” in a phrase such as “disposed about [an element,point or axis]” or “extend about [an element, point or axis]” or “[X]degrees about an [an element, point or axis],” means encircle, extendaround, or measured around. When used in reference to a measurement orin a similar manner, “about” means “approximately,” i.e., in anapproximate range relevant to the measurement as would be understood byone of ordinary skill in the art.

As used herein, “generally” means “in a general manner” relevant to theterm being modified as would be understood by one of ordinary skill inthe art.

As used herein, “substantially” means “by a large amount or degree”relevant to the term being modified as would be understood by one ofordinary skill in the art.

As used herein, “at” means on and/or near relevant to the term beingmodified as would be understood by one of ordinary skill in the art.

As used herein, a “standard beverage can” or “standard beverage canbody” means a generally cylindrical, aluminum can body for atwelve-ounce beverage such as, but not limited to, soda or beer. A“standard beverage can” includes, but is not limited to, a “202 beveragecan” and cans having a similar shape. See,http://www.cancentral.com/beverage-cans/standards.

As used herein, a “dynamic” element is an element that moves during theformation of a can body. Conversely, a “static” element is an elementthat does not move during the formation of a can body.

As used herein, “cooperative” cam surfaces mean two cam surfaces thatextend generally parallel to each other and which are structured to be,and/or are, operatively coupled to the same element or assembly. Forexample, the inner radial surface and the outer radial surface on agenerally toroid cam body wherein the two surfaces impart a motion tothe same element or assembly are “cooperative” cam surfaces. That is,the inner radial surface and the outer radial surface extend generallyparallel to each other. It is understood that the “cooperative” camsurfaces do not necessarily operatively engage the other element orassembly at the same time. That is, when the “cooperative” cam surfacesare defined by a ridge, the “cooperative” cam surfaces do notoperatively engage the other element or assembly at the same time.Conversely, when the “cooperative” cam surfaces are defined by a groove,the “cooperative” cam surfaces selectively, operatively engage the otherelement or assembly at the same time. That is, when the “cooperative”cam surfaces are defined by a groove, the “cooperative” cam surfaces, orportions thereof, are structured to both operatively engage the otherelement or assembly at the same time, or, are structured to individuallyoperatively engage the other element or assembly at a given time.

As used herein, a “direct” [ram] drive assembly means a drive assemblyfor a ram assembly wherein a rotational motion is converted to areciprocal motion without a pivoting construct such as, but not limitedto, a swing arm. Further, a “direct” [ram] drive assembly means a driveassembly for a ram assembly wherein a rotational motion is converted toa reciprocal motion without a gear box structured to convert rotationalmotion to a reciprocal motion. That is, to be a “direct” drive assembly,the moving elements of the drive assembly either rotate with, orotherwise correspond to the rotation of, a motor output shaft, or, movegenerally linearly with the ram assembly. As used herein, to “rotatewith, or otherwise correspond to the rotation of, a motor output shaft”does not include a reciprocal pivoting motion that corresponds to therotation of a motor output shaft. As used herein, to “move generallylinearly with the ram assembly” means that an element moves over a paththat is generally parallel to, or aligned with, the path of the ramassembly. As used herein, a pivoting construct such as, but not limitedto, a swing arm cannot “move generally linearly with the ram assembly.”

As used herein, a “single source/[X]-output ram drive assembly” meansthat the drive assembly includes a single motor, or similar constructthat generates motion, that is operatively coupled to [X] formingassemblies where “[X]” is an integer greater than one. Further, a“single motor” means a single construct or assembly that generatesmotion and which is the only such construct that is operatively coupledto the forming assemblies. That is, as a counter example, a bodymakerwith a drive assembly having two motors disposed in an enclosure whereineach motor is coupled to a ram may be described as having a single“drive assembly” (as the motors are disposed in an enclosure), but thedrive assembly is not a “single source/[X]-output ram drive assembly”because neither motor is the “single construct or assembly thatgenerates motion and which is the only such construct that isoperatively coupled to the forming assemblies.” Stated alternately,merely coupling multiple motors to a housing or similar construct doesnot convert the multiple motors into a “single source/[X]-output ramdrive assembly.”

As used herein, a “prime axis of rotation” for a bodymaker ram driveassembly means an axis of rotation of a rotating ram drive assemblyelement wherein that element is operatively coupled to a plurality ofram assemblies/ram bodies. It is noted that in a bodymaker driveassembly with a crank operatively coupled to two swing arms, and eachswing arm coupled to separate connecting rods, and each connecting rodcoupled to a separate ram assembly/ram body, the couplings between theconnecting rod and a ram assembly/ram body is not a “prime axis ofrotation” as the connecting rod is operatively coupled to a single ramassembly/ram body. Further, a “prime axis of rotation” means that therotating element rotates rather than pivots. That is, for example, abodymaker crank may have a “prime axis of rotation” but a bodymakerpivoting swing arm can never have a “prime axis of rotation.”

As noted above, a ram body moves between a retracted, first position andan extended, second position. Further, a ram body moves over a path witha number of medial positions between the first position and the secondposition. Thus, as used herein, a ram assembly or a ram body in a“medial position” means that the ram assembly or a ram body is disposedat a position between the first position and the second position.Further, a ram assembly or a ram body in a “medial position” means thatthe ram assembly or the ram body is moving toward either the firstposition or the second position. The direction the ram assembly or theram body is moving is, when needed, indicated by the terms “forward” or“rearward.” That is, when the ram body is moving toward the secondposition and is in a medial position, the ram body is, as used herein,in a “forward” medial position. The term “forward” indicates thedirection associated with the ram assembly or a ram body in a medialposition. Conversely, when the ram assembly or the ram body is movingtoward the first position and is in a medial position, the ram assemblyor the ram body is, as used herein, in a “rearward” medial position.That is, the term “rearward” indicates the direction associated with theram assembly or the ram body in a medial position. As noted, the terms“forward” and “rearward” are used when needed for clarity. Thus, as usedherein, the statement that, “no two ram bodies are in the same medialposition at one time” includes a configuration wherein two different ramassemblies/ram bodies are at the midpoint between the first and secondpositions, but wherein the two different ram assemblies/ram bodies aremoving in different directions.

Further, it is understood that, and as used herein, when the ram body isexactly at the first or second position, the ram body is not movingforward or rearward; thus, a ram body at the first or second positiondoes not have an associated direction. Further, a medial “position” isselectively identified by “[X] %” wherein the percentage means theportion of the path between the two end positions. That is, for example,a ram body at the “forward 25%” position means that the ram body ismoving toward the second position and has traveled 25%, i.e.,one-quarter, of the distance between the first and second position. As afurther example, a ram body at the “rearward 50%” position means thatthe ram body is moving toward the first position and has traveled 50%,i.e., one-half, of the distance between the first and second position.Further, a ram assembly that is in a “forward” medial position is,depending upon the position of the blank/cup, in a “forming” position.That is, as used herein, the “forming” position occurs when theblank/cup is moving through the bodymaker die pack.

Referring now to FIGS. 2-6 , a can bodymaker 10 in accordance with oneexample embodiment of the disclosed concept is shown. The bodymaker 10includes a forming system 12 and a mounting assembly 14. The formingsystem 12 includes a number of forming assemblies 16 (four are shown inthe example of FIGS. 2-6 , labeled 16A-16D) and a ram drive assembly300. In one exemplary embodiment, the bodymaker 10 and/or each formingassembly 16 is structured to, and does, form standard beverage canbodies. The mounting assembly 14 is structured to, and does, support thenumber of forming assemblies 16. The mounting assembly 14 is furtherstructured to, and does, rotatably support a cam 330, discussed below,of the ram drive assembly 300. In one exemplary embodiment, the mountingassembly 14 includes a generally planar mounting assembly body 18.

Referring to FIG. 3 , the mounting assembly body 18 is oriented to begenerally horizontal and includes an upper, first surface 22 and alower, second surface 24 opposite the first surface 30. Further, and fora bodymaker 10 including four forming assemblies 16A, 16B, 16C, 16D, themounting assembly body 18 is generally square. It is understood that theshape of the mounting assembly body 18 may be varied so long as themounting assembly body 18 is structured to support the number of formingassemblies 16. In an exemplary embodiment, the mounting assembly body 18defines a generally centrally disposed passage 20 that extends betweenthe first and second surfaces 22 and 24 of the mounting assembly body18.

Continuing to refer to FIG. 3 , in the exemplary embodiment shown, themounting assembly 14 further includes a number of depending element(s)26 disposed at the perimeter of the mounting assembly body 18. If thereis a single mounting assembly depending element 26 extending about theperimeter of the mounting assembly body 18, the single mounting assemblydepending element 26 forms a housing 28 defining an enclosed space 30under the mounting assembly body 18. If there are a plurality ofrelatively thin, spaced separate mounting assembly depending elements26, the separate mounting assembly depending elements 26 are identifiedherein as “legs,” similar to table legs. The mounting assembly dependingelement(s) 26 are structured to, and do, support the mounting assemblybody 18 and elements disposed thereon.

Further, in an example embodiment, the first surface 22 of the mountingassembly body 18 defines a number of recesses 34 (FIGS. 4 and 6 ), eachrecess 34 being for a corresponding forming assembly 16. In an exemplaryembodiment, each recess 34 is a “machined” recess 34. As used herein, a“machined” recess means a recess having contours structured tospecifically position a forming assembly 16 on the mounting assemblybody 18, and thus specifically position the forming assembly 16 relativeto the ram drive assembly 300 and the cam 330. As used herein,“specifically position” means to position a forming assembly 16 relativeto the ram drive assembly 300 and the cam 330 in a manner whereinfurther positioning of the forming assembly 16, and/or elements thereof,relative to the ram drive assembly 300 is not required. That is, whiletypically not mentioned in references/patents, it is well known that theposition of elements of a forming assembly 16 are adjusted followinginstallation so as to ensure proper alignment of the elements. Thus,unless the lack of adjustment of the forming assembly 16 (or elementsthereof) relative to the ram drive assembly 300 (or elements thereof) isspecifically mentioned in a reference/patent, then the reference/patentdoes not disclose a configuration wherein the forming assembly 16,and/or elements thereof, are “specifically position[ed].” That is,unless the lack of adjustment of the forming assembly 16, and/orelements thereof, is specifically mentioned in a reference/patent, thenthe reference/patent does not disclose a “machined” recess, as usedherein.

Further, in another exemplary embodiment, each recess 34 includes anumber, and as shown a plurality, of guide pin passages 36 defined in,and extending through the mounting assembly body 18. Each guide pinpassage 36 has a cross-sectional area structured to accommodate a guidebushing 37. Each guide bushing 37 includes a toroid body 38. Each guidebushing 37 is disposed in a corresponding passage 36. Each guide bushing37 is structured to allow a guide pin 39 to be passed therethrough.

The forming assemblies 16 are substantially similar and as such only oneis described in detail herein. As previously mentioned, it is noted thatthe different forming assemblies 16 shown in the Figures are identifiedby additional letters. Thus, when there are four forming assemblies 16,such as shown in the example of FIG. 2 , the separate forming assemblies16 are identified as forming assemblies 16A, 16B, 16C, 16D. Thisnumbering convention applies to the elements of the forming assemblies16A, 16B, 16C, 16D as well. That is, while the generic, single formingassembly 16 is described as having a die pack 56, the first formingassembly 16A has a die pack 56A and the second forming assembly 16B hasa die pack 56B, and so forth.

Referring now to FIGS. 3 and 4 , a forming assembly 16 includes astationary assembly 42 and a moving assembly 44. In one exampleembodiment, not shown, the stationary assembly 42 is coupled, directlycoupled, or fixed to the first surface 22 of the mounting assembly body18, and the moving assembly 44 is movably coupled to the first surface22 of the mounting assembly body 18 via the stationary assembly 42. Inthe embodiment shown, and as described below, the stationary assembly 42and the moving assembly 44 are a “unified” assembly that is structuredto be, and is, temporarily coupled to the mounting assembly body 18.That is, the elements of the stationary assembly 42 and the movingassembly 44 are coupled, directly coupled, or fixed to each other.Further, the stationary assembly 42 and the moving assembly 44 arestructured to be, and are, temporarily coupled to a stationary assemblybase 50, as discussed below. In this configuration, the forming assembly16 is a unified assembly.

As shown in the example embodiment of FIG. 4 , the stationary assembly42 of the forming assembly 16 includes the stationary assembly base 50,a ram guide assembly 52, a redraw assembly 200, a die pack 56 and adomer 58. The base 50 includes a generally planar member 60 with anumber of upwardly depending, generally planar supports 62. The planarmember 60 is structured to, i.e., is machined to, substantiallycorrespond to the recess 34 defined in the first surface 22 of themounting assembly body 18. The planar member 60 has a proximal end 64and a distal end 66. When the forming assembly 16 is operatively coupledto the ram drive assembly 300, the proximal end 64 of the planar member60 is the end closer to the cam 330 of the ram drive assembly 300 andthe distal end 66 of the planar member 60 is the end further from thecam 330 of the ram drive assembly 300.

In one example embodiment, the planar member 60 includes a number, andas shown a plurality, of guide pin passages 68 extending through theplanar member 60 of the base 50 of the stationary assembly 42. Thenumber of guide pin passages 68 are disposed in a pattern correspondingto the guide pin passages 36 of the recess 34 of the mounting assemblybody 18 previously discussed. Each guide pin passage 68 has across-sectional area structured to accommodate a guide bushing 69. Thenumber of guide pin passages 36 of the recess 34 and the number of guidepin passages 68 of the planar member 60, along with the associated guidebushings 37 and 69 thereof, are structured to position each formingassembly 16 relative to the cam 330. That is, in an embodiment includingthe guide pin passages 36, 68, when a planar member 60 is disposed in amachined recess 34, each guide pin passage 36 generally aligns with anassociated guide pin passage 68. Further, when guide pins 39 are passedthrough the associated guide pin passages 36, 68 (and the associatedbushings 37, 69), the planar member 60 is brought into alignment withthe cam 330. Although two sets of associated guide pin passages 36 and68 are shown, it is to be appreciated that the quantity of associatedguide pin passages 36 and 68 may be varied without varying from thescope of the disclosed concept.

The supports 62 of the base 50 include at least a domer support 70. Thedomer support 70 includes a generally planar body 72 that may be aseparate member coupled to the planar member 60, or may be formedunitarily with the planar member 60. As shown, the body 72 of the domersupport 70 extends generally laterally relative to a longitudinal axis Lof a ram body 122, discussed below. The supports 62 of the base 50further include a die pack support 74 which, as shown, is a frame 76that is raised above the plane of the planar member 60 of the base 50 ofthe forming assembly 16. Further, the supports 62 of the base 50 includea ram guide assembly support 78 that is structured to, and does, supportthe ram guide assembly 52 of the stationary assembly 42. As shown, theram guide assembly support 78 includes a generally planar body 79 thatmay be a separate member coupled to the planar member 60, or may beformed unitary with the planar member 60. The body 79 extends generallyparallel to the plane of the body 72 of the domer support 70.

Continuing to refer to FIG. 4 , as well as to FIG. 7B, the ram guideassembly 52 includes a housing 80 defining a passage 81. A number ofbearing assemblies 82 such as, but not limited to,hydrostatic/hydrodynamic bearing assemblies 84 (which also define apassage, not numbered) are disposed in the housing 80. The bearingassemblies 84 are structured to, and do, support the ram body 122 as theram body 122 reciprocates, as described below. The ram guide assembly 52further includes a seal pack assembly 86 (FIG. 4 ) that is structuredto, and does, substantially remove the hydrostatic/hydrodynamic bearingfluid from the ram body 122 (discussed below), as is known.

As shown in FIG. 4 and FIGS. 8A-8C, the redraw assembly 200 includesboth stationary elements and moving elements and is included herein withthe stationary assembly 42 of the forming assembly 16. In an exemplaryembodiment, the redraw assembly 200 includes a hold down piston 202(shown schematically) and a blank (cup) holder 204. The blank holder 204is coupled, directly coupled, or fixed to the hold down piston 202 andmoves therewith. The hold down piston 202 and the blank holder 204 eachinclude a generally toroid body 206, 208, respectively, each defining acentral passage (not numbered) that is sized to allow a ram body 122 topass therethrough. The redraw assembly 200 also includes a servo-motor209, or similar construct, that is structured to move the hold downpiston 202, and therefore the blank holder 204, in a generallyreciprocal motion. That is, the hold down piston 202 and the blankholder 204 are structured to move/translate in a linear fashion (e.g.,along a translation axis 229) between a first positioning, wherein thehold down piston 202 and the blank holder 204 are spaced from the diepack 56, and, a second positioning wherein the hold down piston 202 andblank holder 204 are disposed immediately adjacent the die pack 56. Asis known, a cup feed assembly 108 (discussed below) or similarconstruct, positions a cup or blank at the mouth of the die pack 56. Theblank holder 204 maintains the cup/blank in this position until the rambody 122 engages the cup/blank and moves the cup/blank through the diepack 56.

In an exemplary embodiment, such as illustrated in FIG. 4 and FIGS.8A-8C, a servo-motor 209 is coupled to a number of cam disks 214, 214′(two are shown in the illustrated example, further, it is noted that thecam 330 of the ram drive assembly 300, discussed below, is identified asthe “cam 330”; while, as used herein, the “cam disk 214” is identifiedas the “cam disk 214”) and the hold down piston 202 and the blank holder204 are coupled to, or biased against (i.e., away from the die pack 56)the cam disk 214 via a number of suitable biasing members 210 (e.g.,spring(s) or other suitable arrangement(s)). In the exemplary embodimentshown in FIG. 4 , the cam disk 214 is a generally planar body that isrotatable about a rotation axis 215 (disposed perpendicular to theaforementioned translation axis 229 of the hold down piston 202 and theblank holder 204) by the servo motor 209. The hold down piston 202 andthe blank holder 204 are biased against the edge surface 211 of the camdisk 214. The edge surface 211 of the cam disk 214 defines a forwardstroke portion 216, a forward dwell portion 218, a backward strokeportion 220 and a backward dwell portion 222. That is, as the forwardstroke portion 216 engages the hold down piston 202, the hold downpiston 202, and therefore the blank holder 204, moves from the firstposition to the second position (i.e., toward the die pack 56),compressing the number of biasing members 210. As the forward dwellportion 218 engages the hold down piston 202, the hold down piston 202,and therefore the blank holder 204, are maintained in the secondposition. As the backward stroke portion 220 engages the hold downpiston 202, the hold down piston 202, and therefore the blank holder204, move from the second position to the first position (i.e., awayfrom the die pack 56) due to the force of the number of biasing members210. As the backward dwell portion 222 engages the hold down piston 202,the hold down piston 202, and therefore the blank holder 204, aremaintained in the first position. Thus, the hold down piston 202, andtherefore the blank holder 204 moves between the first and secondpositions while dwelling at those positions between periods of motion.This allows a cup/blank to be positioned between the blank holder 204and the die pack 56 while the blank holder 204 dwells at the firstposition, and, allows the blank holder 204 to maintain a cup/blank atthe die pack 56 while the blank holder 204 dwells at the secondposition. In another embodiment, not shown, the ram drive assembly 300includes a linkage that moves the hold down piston 202 and the blankholder 204 between the first and second positions in a similar manner,i.e., moving with dwell periods in between motion periods, thuseliminating the cam disk 214.

FIGS. 9A-9C show another exemplary embodiment of a redraw assembly 200′including a hold down piston 202 and blank holder 204 similar to redrawassembly 200. The hold down piston 202 and blank holder 204 are slidablycoupled to the die pack support 74 (e.g., via a number of linear bearingpins 226 and cooperating linear bearing bushings 228) such that the holddown piston 202 and blank holder 204 are readily translatable along atranslation axis 229 disposed perpendicular to the rotation axis 215.Redraw assembly 200′ functions similarly to the redraw assembly 200 ofFIG. 4 except the redraw assembly 200′ utilizes a cam disk 214′ having agroove 230′ that is engaged by a roller member 232 or other suitableconstruct that is coupled to the hold down piston 202. Optionally,redraw assembly 200′ further utilizes a second cam disk 214″ having agroove 230″ that is likewise engaged by a second roller member 232′. Inoperation, one or both of cam disks 214′ and 214″ are rotated about therotation axis 215 by a servo-motor 212, or similar construct that isdirectly coupled the servo motor 212 (as shown) or coupled thereto via abelt or other suitable arrangement. As one or both of cam disks 214′ and214″ are rotated, the grooves 230′ and 230″ thereof interact with theroller members 230 and 232, thus causing the hold down piston 202 andthe blank holder 204 to translate back and forth along the translationaxis 229 among a first positioning, wherein the hold down piston 202 andthe blank holder 204 are spaced from the die pack 56, and a secondpositioning, wherein the hold down piston 202 and the blank holder 204are disposed immediately adjacent the die pack 56.

Moving on to the die pack 56, the die pack 56 includes a number, andtypically a plurality, of dies (none numbered). Each die includes agenerally toroid body (none shown) having a central opening sized toiron and otherwise form the cup/blank into a can body (not shown). Thatis, as is well known, the die pack 56 is structured to reform/form acup/blank disposed on a punch 124/ram body 122 into a can body(discussed below). As such, the dies of the die pack 56 define a formingpassage 100 having an upstream, proximal end 102 (or “mouth” 102) and adownstream, distal end 104.

The redraw assembly 200 is disposed at the proximal end 102 of theforming passage 100. Further, and as is known, the die pack 56 includes,or is disposed adjacent or immediately adjacent, a stripper assembly 106structured to strip, i.e., remove, a can body from the ram body 122during the return stroke, as described below. That is, the stripperassembly 106 is disposed at the distal end of the forming passage 100.

In an exemplary embodiment, the die pack 56 further includes a cup (orblank) feed assembly 108. In an exemplary embodiment, the cup feedassembly 108 includes a servo-motor and a rotary support (neithernumbered). Cups, or blanks, are disposed on the cup feed assembly rotarysupport. The cup feed assembly servo-motor is structured to, and does,rotate the cup feed assembly rotary support so that a cup (or blank) ispositioned at the proximal end 102 of the forming passage 100 of the diepack 56 prior to the ram body 122 moving through the die pack 56, asdiscussed below.

The domer 58 includes a mounting assembly 110 and a domer body 112. Themounting assembly 110 is structured to be coupled to the domer support70. The mounting assembly 110 is further structured to adjustablysupport the domer body 112. The domer body 112 includes a domed surface114 having a vertex 116. The domed surface 114/vertex 116 is disposedfacing, and generally aligned with, the forming passage 100 of the diepack 56, as is known.

Referring to FIGS. 4-6 , the moving assembly 44 of the forming assembly16 includes a ram assembly 120 and a cam follower assembly 150. The ramassembly 120 includes an elongated body 122 (hereinafter, and as usedherein, “ram body” 122) and a punch 124 (hereinafter, and as usedherein, “punch” 124). The ram body 122 has a proximal, or first, end126, a medial portion 125 and a distal, or second, end 128. As is known,the punch 124 is coupled, directly coupled, or fixed to the ram bodydistal end 128. As is known, the distal end 128 has a smallercross-sectional area relative to the proximal end 126 and the medialportion 125. In an exemplary embodiment, the punch 124 has across-sectional area that is substantially similar to the proximal end126 and the medial portion 125. Thus, there is a generally, or asubstantially, smooth transition between the punch 124 and the ram body122. The cam follower assembly 150 is disposed at, and coupled to, theproximal end 126 of the ram body 122.

Further, in an exemplary embodiment, the ram body 122 is generallyhollow. That is, the ram body 122 defines a cavity 130. The distal end128 of the ram body 122 includes a passage 129 that is in fluidcommunication with the cavity 130. Further, if a punch 124 is used, thepunch 124 also includes an axially extending passage 127. That is, thepassage 129 of the ram body 122 (and, if included, the punch passage127) extends from the axial surface of the distal end 128 of the rambody 122 to the cavity 130. The cavity 130 is selectively in fluidcommunication with a pressure assembly (discussed below). The pressureassembly is structured to, and does, generate a positive and/or anegative fluid pressure. As is known, the cavity 130 of the ram body 122is selectively in fluid communication with a negative fluid pressurewhen the ram body 122 is moving forward (i.e., away from the ram driveassembly 300). In this configuration, a negative fluid pressure biasesthe cup/blank toward the ram body 122 and/or punch 124. When the rambody 122 is moving backward (i.e., toward the ram drive assembly 300), apositive pressure helps to remove the now formed can body from the rambody 122/punch 124. As the ram body 122 is one of the longer elements ofthe forming assembly 16, as used herein, the longitudinal axis L of theram body 122 is also the longitudinal axis of the forming assembly 16.

Referring to FIGS. 4, 5 and 7A-7D, the cam follower assembly 150 of themoving assembly 44 of a forming assembly 16 includes a slider 152 and anumber of cam follower members 154 (two are shown in the example). In anexemplary embodiment, the slider 152 includes a slider body 160, a lowerframe portion 162 extending downward from the slider body 160, and anupper frame portion 164 extending upward from the slider body 160. Inthe example illustrated, slider body 160 is disposed generally parallelto the plane of the first surface 22 of the mounting assembly body 18,i.e., generally horizontally as shown.

The lower frame portion 162 of the slider body 160 includes a firstmember 162A extending downward generally from at or near a first edge160A of slider body 16, a second member 162B extending downwardgenerally from at or near a second edge 160B of slider body 160 oppositethe first edge 160A, and a third member 162C extending between the firstand second members 162A and 162B and spaced a distance below slider body160. In the example shown in FIG. 7D, the third member 162C extendsgenerally horizontally, parallel to the slider body 160, between firstand second members 162A and 162B. Each of the first, second, and thirdmembers 162A-162C may be formed integrally as portions of a singleunitary member, such as shown in the example of FIG. 7D, oralternatively may be formed as separately and then coupled together viaany suitable method (e.g., bolts, welding, etc.).

The upper frame portion 164 of the slider body 160 includes a firstmember 164A extending upward generally from at or near the first edge160A of slider body 160, a second member 164B extending upward generallyfrom at or near the second edge 160B of slider body 160, and a thirdmember 164C extending between the first and second members 164A and 164Band spaced a distance above slider body 160. Each of the first, second,and third members 164A-164C may be formed integrally as portions of asingle unitary member, such as shown in the example of FIG. 7D, oralternatively may be formed as separately and then coupled together viaany suitable method (e.g., bolts, welding, etc.).

Continuing to refer to FIGS. 7A and 7D, the cam follower assembly 150further includes a cam follower bearing assembly 165 having a number ofhydrostatic/hydrodynamic bearing pads 166 which are positioned andstructured to engage with corresponding, cooperatively positioned,bearing members 167 provided as part(s) of stationary assembly 42. Eachbearing member 167 includes a bearing surface 168 upon which eachbearing pad 166 is positioned and structured to slide. Ahydrostatic/hydrodynamic bearing assembly is discussed in detail in U.S.Pat. No. 10,137,490 and the disclosure of the hydrostatic/hydrodynamicbearing assembly therein is incorporated herein by reference. Eachbearing pad 166 includes a recessed bearing pocket 169 (two of which,169A and 169C, are numbered in FIG. 7D) that is structured to generallyhouse a pressurized supply of oil or other suitable bearing fluid (notshown) provided therein (as discussed further below).

Prior art drive assemblies, such as drive assembly 2 previouslydiscussed in regard to FIG. 1 exert vertical forces on ram bodies, suchas ram body 7B, that must be addressed/managed by bearings thatgenerally completely surround the ram body. Such vertical forces canresult in ram “droop.” However, unlike such prior art arrangements,arrangements utilizing a cam drive such as described herein aregenerally only subjected to moderate lateral forces and are notsubjected to any meaningful vertical forces. Hence, the cam followerbearing assembly 165 is of unique design as compared to knownarrangements. In the example illustrated in FIGS. 7A-7D, the camfollower bearing assembly 165 includes three generally planarhydrostatic/hydrodynamic bearing pads 166: a first bearing pad 166Acoupled, directly coupled, or fixed to an outward facing face of firstmember 164A; a second bearing pad 166B coupled, directly coupled, orfixed to an outward facing face of second member 164B (i.e., facing inthe opposite direction from first bearing pad 166A); and a third bearingpad 166C coupled, directly coupled, or fixed to an upward facing face ofthird member 164C. In such example, the cam follower bearing assembly165 also includes three bearing members 167A, 167B and 167C,respectively having bearing surfaces 168A, 168B and 168C. Moreparticularly, the first bearing member 167A is fixedly coupled to thestationary assembly base 50 of the forming assembly 16 such that thebearing surface 168A thereof is positioned outward, above, and parallelto the longitudinal axis L of the ram body 122 of the forming assembly16, and generally perpendicular to the stationary assembly base 50. Thesecond bearing member 167B is fixedly coupled to the stationary assemblybase 50 of the forming assembly 16 such that the bearing surface 168Bthereof is positioned outward, above, and parallel to the longitudinalaxis L of the ram body 122 of the forming assembly 16; generallyperpendicular to the stationary assembly base 50, and facing the bearingsurface 168A of the first bearing member 167A. The third bearing member167C is fixedly coupled to the stationary assembly base 50 of theforming assembly 16 such that the bearing surface 168C thereof ispositioned directly above and parallel to the longitudinal axis L of theram body 122 of the forming assembly 16, generally parallel to thestationary assembly base 50, and perpendicular to each of the bearingsurfaces 168A and 1688 of the first bearing member 167A and the secondbearing member 167B. Accordingly, as can be readily appreciated from thesectional view of FIG. 7C, the three bearing members 167A-167C arepositioned so as to form a downward opening channel (with the bearingsurfaces 168A-168C facing inward) that is disposed about the upper frameportion 164 of the slider body 160 and the outward facing bearings pads166A-166C thereof. From such view, it can also be readily appreciatedthat such cam follower bearing assembly 165 does not include any bearingmembers 167 or surfaces 168 providing upward support to slider 152, asnone are needed in such arrangement as compared to prior artarrangements. In one exemplary embodiment in accordance with thedisclosed concept, each of the bearing surfaces 168A-168C are ground toa 4-8 micron surface finish and parallelism and squareness within0.0002″.

As previously discussed, the ram body 122 is generally hollow anddefines the cavity 130 therein that is selectively in fluidcommunication with a pressure assembly. Such communication between apressure assembly (not shown) and cavity 130 of ram body 122 is providedvia a flexible conduit or hose 170 that extends between a lower rotaryseal 170A that is coupled to mounting assembly body 18 or any othersuitable fixed location for connection to the aforementioned pressureassembly, and an upper rotary seal 170B that is coupled to the lowerframe portion 162 of the slider body 160. The upper rotary seal 170B isin fluid communication with the cavity 130 of the ram body via anysuitable conduit arrangement provided as a part of cam follower assembly150. A shock absorber arrangement 171 is provided about hose 170 tominimize hose whipping resulting from the reciprocating movement of camfollower assembly 150.

As also previously discussed, each bearing pad 166 includes a recessedbearing pocket 169 that is structured to generally house a pressurizedsupply of oil or other suitable bearing fluid (not shown) providedtherein. Such supply of oil or other suitable bearing fluid is providedin a similar manner as the conductive pressure arrangement justdescribed. In other words, the supply of oil or other suitable bearingfluid is provided to a second upper rotary seal 172B (see FIGS. 7B and7C) that is coupled to the lower frame portion 162 of the slider body160. The supply is provided via a hose coupled to a second lower rotaryseal (neither of which are shown) positioned similarly to hose and lowerrotary seal 170 and 170A (and shock absorber arrangement 171) that iscoupled to a suitable source of the supply (also not shown). The supplyof oil or other suitable bearing fluid is communicated from the secondupper rotary seal 172B to the recessed bearing pocket 169 of each of thenumber of bearing pads 166A, 166B, 166C via any suitable conduitarrangement provided as a part of cam follower assembly 150 connected toan inlet 173 (see FIG. 7D) provided in each bearing pocket 169. In oneexemplary embodiment in accordance with the disclosed concept, an oilflow is injected into a manifold (not numbered) at a pressure ofapproximately 1000 psi. From the aforementioned manifold the oil flow isfed to each bearing pad 166A, 166B, 166C. The oil flow is controlled byleejets (i.e., calibrated orifices). It is to be appreciated that sucharrangement of bearing pads 166A, 166B, 166C, corresponding bearingsurfaces 168A, 168B, 168C, and oil flow results in an oil film betweenthe corresponding bearing pads 166A, 166B, 166C and bearing surfaces168A, 168B, 168C that prevents any metal to metal contact and thusprovides for smooth sliding of cam follower assembly 150 along bearingmembers 167A, 167B, 167C and thus smooth translations relative to thestationary assembly base 50 of the forming assembly 16.

Referring now to FIG. 5 , the slider body 160 includes a number ofpassages (not collectively numbered) defined therethrough. The passagesinclude a number of cam follower mounting passages, two shown 174 and175. If there are two cam follower mounting passages 174, 175, the camfollower mounting passages 174, 175 are disposed generally along a linethat, when the forming assembly 16 is coupled to the mounting assembly14, is generally a radial line extending outward from the passage 20 ofthe mounting assembly body 18 and aligned above the longitudinal axis Lof the ram body 122 of forming assembly 16. Another passage definedthrough slider body 160 is an alignment pin passage 178 positionedgenerally adjacent the end of slider body 160 opposite ram body 122.

The cam follower members 154 are structured to be, and are, operativelyengaged by the cam 330 of the ram drive assembly 300. Statedalternately, the cam 330 is structured to be, and is, operativelycoupled to the cam follower members 154 of the moving assembly 44 ofeach forming assembly 16 and is, therefore, operatively coupled to eachram assembly 120 and/or forming assembly 16.

In one embodiment, not shown, the cam follower members 154 are rigidbearings. In the embodiment shown in FIGS. 2-6 and 7A-7D, the camfollower members 154 are roller bearings 180 (hereinafter, and as usedherein, the “cam follower roller bearings” 180). As shown, and in anexemplary embodiment, each cam follower roller bearing includes an axle184 and a wheel 186 (see FIG. 5 ). Further, and in an exemplaryembodiment, one of the cam follower roller bearings 180 includes aneccentric bushing 187. The eccentric bushing 187 includes a hollowtubular body 188 that is structured to fit within cam follower mountingpassage 175 (or alternatively passage 174). The tubular body 188 has agenerally cylindrical outer surface 190 having a first center (notnumbered), and, a generally cylindrical outer surface 192 having asecond center (not numbered). The first and second centers noted in theprior sentence are not aligned. That is, the first and second centersnoted above are offset from each other. In this configuration, theeccentric bushing 187 includes a portion with a maximum thickness,hereinafter the “thicker” side 188′ of the eccentric bushing 187, and, aportion with a minimum thickness, hereinafter the “thinner” side 188″ ofthe eccentric bushing 187. Further, the eccentric bushing 187 includesan orientation tab 194 that extends generally radially from the outersurface 190 of the tubular body 188. In this configuration, theeccentric bushing 187 is structured to, and does, move the associatedroller bearing wheel 186 between a spaced, first position and a close,second position, as discussed below.

Thus, as used herein, a “forming assembly” 16 includes at least a diepack 56, a domer 58, and a ram body 122. Further, a “forming assembly”16 selectively includes additional elements such as, but not limited to,a ram guide assembly 52 and a redraw assembly 200.

A forming assembly 16 is assembled as follows. The ram guide assembly52, the redraw assembly 200, and the die pack 56 are coupled, directlycoupled, or fixed to the base planar member 60, i.e., the stationaryassembly base 50. The domer 58 is coupled, directly coupled, or fixed tothe domer support 70, i.e., which, as previously discussed, is coupledto, or formed as a unitary portion of, the stationary assembly base 50.Generally, the ram guide assembly 52 is disposed closest to the passage20 of the mounting assembly body 18. The redraw assembly 200 is disposedadjacent the ram guide assembly 52. The die pack 56 is disposed adjacentthe ram guide assembly 52 with the cup feed assembly 108 disposedbetween the redraw assembly 200 and the die pack 56. Further, as notedabove, the stripper assembly 106 is disposed at the distal end 104 ofthe forming passage 100 of the die pack 56. Finally, the domer 58 isspaced from the die pack 56 and/or stripper assembly 106. That is, thedomer 58 (or stripper assembly 106) is spaced from the die pack 56 by adistance that is at least the length of a can body and, as shown, adistance that is greater than at least the length of a can body. In oneembodiment, and in the configuration described above, the stationaryassembly 42 of the forming assembly 16 is complete.

The moving assembly 44 of the forming assembly 16 is assembled asfollows. The proximal end 126 of the ram body 122 is coupled, directlycoupled, or fixed to the slider 152 of the cam follower assembly 150. Asshown, and in an exemplary embodiment, the proximal end 126 of the rambody 122 is coupled to the lower frame portion 162 of the slider body160. The punch 124 is disposed over and coupled, directly coupled, orfixed to the distal end 128 of the ram body 122. In this configuration,the longitudinal axis L of the ram body 122 is generally, orsubstantially, aligned with the longitudinal axis of the passage 81, theredraw assembly 200, and the forming passage 100 of the die pack 56.Further, the longitudinal axis L of the ram body 122 is generally, orsubstantially, aligned with the vertex 116 of the domed surface 114 ofthe domer body 112. That is, if the longitudinal axis L of the ram body122 were extended, it would pass through, or be immediately adjacent thevertex 116 of the domed surface 114 of the domer body 112.

In this configuration, and in one embodiment, the forming assembly 16 iscomplete. Further, as noted above, the forming assembly 16 is a“unified” assembly. Further, it is understood that as the formingassembly 16 is assembled, the various elements are positioned to be inproper alignment, as is known in the art. That is, for example, the rambody 122 is adjusted/repositioned until the longitudinal axis L of theram body 122 is generally, or substantially, aligned with thelongitudinal axis of the passage 81 of the housing 80 of the ram guideassembly 52 and the longitudinal axis of the forming passage 100 of thedie pack 56. As the forming assembly 16 is a “unified” assembly, theelements thereof remain aligned with each other. That is, when theforming assembly 16 is removed from the mounting assembly 14, theelements thereof are not separated. As such, the elements of the formingassembly 16 do not have to be adjusted so as to be in alignment eachtime the forming assembly 16 is installed. A forming assembly 16 thatmaintains the alignment of the elements, i.e., wherein the elements ofthe stationary assembly 42 and the moving assembly 44 are not separated,during an installation is, as used herein, an “aligned” unified formingassembly 16. A unified forming assembly 16 or an aligned unified formingassembly 16 solves the problem(s) noted above.

As shown in FIGS. 2-3 , the ram drive assembly 300 of bodymaker 10 isstructured to, and does, move the moving assembly 44 of the formingassembly 16, i.e., the ram assembly 120 or the ram body 122, between aretracted (i.e., toward the ram drive assembly 300), first position,wherein the ram body 122 is not disposed in the forming passage 100 andthe distal end 128 of the ram body 122 is spaced from an associated diepack 56, and, an extended (i.e., away from the ram drive assembly 300),second position wherein the ram body 122 is disposed in the formingpassage 100 and the distal end 128 of the ram body 122 is adjacent anassociated domer 58. The ram drive assembly 300, as detailed below, doesnot include either a crank, a swing arm, and/or pivoting connectingrods. This solves the problem(s) noted above.

Referring to FIG. 3 , the ram drive assembly 300 includes a motor 310and a cam 330 that is rotated around a prime axis of rotation 330 by themotor 310. The motor 310 includes a rotating output shaft 312. In anexemplary embodiment, the motor 310 is disposed below the mountingassembly body 18 within the enclosed space 30 defined by housing 28. Asshown, a primary axle 314 is generally disposed within the hollowmounting assembly enclosed space 30 and rotatable about prime axis 333.The motor output shaft 312 is operatively coupled to the primary axle314, e.g., by a gear box 315. As such, the primary axle 314 is alsoidentified herein as a part of the motor 310. The primary axle 314includes an elongated axle body 316 having an upper, first end 318 and alower, second end (not numbered) coupled to the gear box 315. The lowersecond end of axle body 316 may be selectively coupled to the gear box315 via a suitable clutch arrangement that provides for axle body 316 tobe selectively engaged or disengaged from the gear box 315, and thusmotor 310. The first end 318 of the axle body 316 extends through thepassage 20 of the mounting assembly body 18. The first end 318 of theaxle body 316 is structured to be, and is, coupled to the cam body 332.A brake arrangement 319 (e.g., a disk brake or other suitablearrangement) is positioned along primary axle 314 for selectivelybringing rotation about prime axis 333 of primary axle 314 and cam body332 to a controlled and timely stop.

The cam 330 of the ram drive assembly 300 includes a body 332 defining,or having, a number of cooperative cam surfaces 334, 336, (two shown)and identified herein as the inner, first cam surface 334 and the outer,second cam surface 336. The cam 330/cam body 332 is structured to, anddoes, impart a reciprocal motion to each forming assembly 16 and, in anexemplary embodiment, to each moving assembly 44 and/or ram assembly120. Further it is noted that, as discussed below, the cam 330 moveswhile each forming assembly 16 is mounted on the mounting assembly 14.That is, the cam 330 is dynamic and each forming assembly 16 isstatically mounted. Thus, the cam body 332 is a “dynamic cam body”. Thissolves the problems noted above. Alternatively, the cam body 332 couldbe fixed or held in a steady state with each forming assembly 16 movingthereabout. In such arrangement, cam body 332 would be a “steady statecam body”.

Further, in an exemplary embodiment, the cam 330/cam body 332 isstructured to, and does, generate a “smooth ironing action” in thedistal end 128 of the ram body 122/punch 124 as the ram body 122/punch124 moves through the die pack 56. As used herein, a “smooth ironingaction” means that the construct that supports the cup, which istypically the distal end 128 of the ram body 122 or punch 124, is notbeing accelerated or decelerated as the construct that supports the cuppasses through the die pack 56. In an exemplary embodiment, the cam body332 includes cooperative cam surfaces 334, 336, discussed below, havinga substantially constant velocity cam profile, discussed below. The camsurfaces 334, 336 with a constant velocity cam profile cause the distalend 128 of the ram body 122 or punch 124 to move at a substantiallyconstant velocity, i.e., no acceleration or deceleration, as the distalend 128 of the ram body 122 or punch 124 pass through the die pack 56.Thus, such a cam 330/cam body 332 is structured to, and does, generate a“smooth ironing action.” This solves the problem(s) noted above.

Further, in an exemplary embodiment, the components (i.e., the ramassembly 120 and cam follower assembly 150) of the moving assembly 44 ofthe forming assembly 16 are of low mass. Use of such a low mass movingassembly 44 with a cam 330 having dwell portions (and thus zeroacceleration and, consequently, zero inertial forces and deformations)at the travel extremes results in zero or essentially zero deformationsin moving assembly 44 and components thereof at virtually any operatingspeed. Hence, once the position of ram assembly 120 is adjusted foroptimum doming position, such positioning will not change with theproduction speed. This solves the problem(s) above.

Further, in an exemplary embodiment, the cam 330/cam body 332 isstructured to be, and is, a “direct operative coupling element.” As usedherein, a “direct operative coupling element” means an element that isstructured to be directly coupled to both the construct that generatesmotion and the ram assembly of a bodymaker. In the embodiment above, theconstruct that generates motion is the motor 310. To be “directlycoupled” to a construct that generates motion, as used herein, meansthat an element is directly coupled to a motor output shaft or amounting on a motor output shaft. As used herein, a “mounting” for amotor output shaft is a construct that rotates with the motor outputshaft and which has a body that is disposed substantially symmetricallyabout the motor output shaft. That is, for example, the crank of a priorart bodymaker is, typically, “directly coupled” to a motor output shaft;the crank, however, does not have a body that is disposed substantiallysymmetrically about the motor output shaft; thus, as used herein, acrank is not a “mounting.” Further, as used herein, the “ram assembly”means the elements that move with, and substantially parallel to, a rambody path of travel. That is, for example, in the prior art arrangementsuch as shown in FIG. 1 , both the carriage 7A and the second connectingrod 6B both move with the ram body 7B, but the second connecting rod 6Bdoes not move with, and substantially parallel to, the ram body 7B pathof travel. Thus, the second connecting rod 68, and similar elements, arenot part of the “ram assembly.” Thus, as described above, the prior artmulti-element linkage, i.e., crank 4/swing arm 5/first connecting rod6A/second connecting rod 6B, does not, and cannot, be a “directoperative coupling element.” That is, such a linkage is not a singleelement and such a linkage is not directly coupled” to a motor outputshaft. Thus, the cam 330/cam body 332 that is structured to be, and is,a “direct operative coupling element” solves the problem(s) noted above.

In one embodiment, the cam body 332 is a generally solid, unitary,planar with an axially extending hub 337 (FIG. 3 ) and a ridge 338extending about the cam body 332 axis of rotation (i.e., prime axis333). In another embodiment such as shown in FIG. 13 , the cam body 332′is a two-part assembly, an outer ring 332A′ disposed about an innersection 332B′. Outer ring 332A′ and inner section 332B′ may be formedfrom different materials and one or both of outer ring 332A′ and 332B′may have one or more apertures or open sections defined therein orthereby to lighten such sections and thus reduce the moment of inertiaof such cam 330′.

Referring again to FIG. 3 , the cam body hub 337 defines a couplingpassage 339. In an exemplary embodiment, the coupling passage 339 istapered and narrows from bottom to top (e.g., see FIG. 3 ). In anexemplary embodiment, the first end 318 of the axle body 316 isstructured to be, and is, coupled to the cam body 332 at the couplingpassage 339. As shown, the cam body ridge 338, in an exemplaryembodiment, extends about the perimeter of the cam body 332. As shown inFIG. 2 , when viewed from above, the ridge 338 of the cam body 332 isnot substantially circular, as discussed in detail below; that is, theridge 338 does not have a substantially consistent radius R relative tothe axis of rotation (i.e., prime axis 333) of the cam body 332, butinstead is varied in a predetermined manner to create desired movementof the moving assembly 44. The overall variation in the radius R (i.e.,the difference between the minimum and maximum value of the radius R,which is equal to the stroke of the ram assembly 120) is dependent onthe height of the can body being produced. In an exemplary embodiment, astroke of 22″ is used to manufacture cans up to 6.5″ tall/long. As usedherein, a generally planar cam body 332 having a ridge 338 extendingabout the perimeter of the cam body 332 is a “disk cam.” In thisembodiment, the ridge 338 includes the inner, first cam surface 334 andthe outer, second cam surface 336. Further, in an exemplary embodiment,the radial width W (FIG. 5 ) of the cam body ridge 338 is generally, orsubstantially, consistent. That is, the distance between the first camsurface 334 and the second cam surface 336 is generally, orsubstantially, consistent. Further, in an exemplary embodiment, the cambody 332 includes a number of alignment passages 344 disposed adjacentthe cam body ridge 338, the purpose of which is discussed below.

In another example embodiment, such as shown in FIGS. 10 and 11 , abodymaker 10B utilizing a “barrel” cam 330B is shown. The bodymaker 108is of a similar arrangement as the bodymaker 10 previously discussed inconjunction with FIGS. 2-6 except the bodymaker 10B only includes twoforming assemblies 16 and includes a ram drive assembly 300B thatincludes/utilizes the “barrel” cam 330B instead of a disk cam.Hereinafter, and in relation to the barrel cam 330B, reference numberssimilar to the embodiment shown in FIGS. 2-6 will be used, but thereference numbers will include the letter “B.” In this embodiment, thecam body 332B is generally cylindrical and includes a groove (not shown)or a ridge (as shown) 338B disposed thereabout on a cylindrical surface(not numbered) of the cam body 332B. The ridge 338B extends generallyaxially while also forming a loop about the cylindrical cam body 332B.In this configuration, the cam body 332B, i.e., the ridge 338B thereon,defines a generally axial first cam surface 334B and a generally axialsecond cam surface 336B. It is understood that, where the ridge 338Breverses direction, the ridge 338B extends generally circumferentiallyaround the cam body 332B rather than axially along the cam body 332B. Inthis embodiment, the opposing sides of the ridge 338B are thecooperative cam surfaces 334B, 336B. It is noted that a ram driveassembly 300 including, or consisting of, these elements does notinclude pivotal couplings. This solves the problem(s) stated above.

In either of such example arrangements, the cooperative cam surfaces334, 336 or 334B, 336B are structured to, and do, operatively engageeach cam follower assembly 150. In the embodiment shown in FIGS. 2-6 ,the cam follower assembly 150 includes two cam follower members 154,i.e., roller bearings 180, also identified herein as first cam followermember 156 and second cam follower member 158. The first cam followermember 156 is disposed adjacent the first cam surface 334. That is, thewheel 186 of the first cam follower member 156 is disposed adjacent tothe first cam surface 334. The second cam follower member 158 isdisposed adjacent the second cam surface 336. That is, the wheel 186 ofthe second cam follower member 158 is disposed adjacent to the secondcam surface 336. Thus, in such embodiment, the first and second camfollower members 156, 158 “sandwich” the cam body ridge 338. That is,the first and second cam follower members 156, 158 are disposed onopposite sides of the cam body ridge 338. In an exemplary embodimentwith a barrel cam having a groove instead of a ridge 334B, there is asingle cam follower member which is structured to be, and is, disposedin the groove.

Further, as shown in FIGS. 10 and 11 , in an exemplary embodiment, thebodymaker 10B has a barrel cam 330B that includes two separate barrelcams 330B′, 330B″ that are coupled, directly coupled, or fixed to theoutput shaft 312B of a motor 310B. It is understood that, in anexemplary embodiment, each barrel cam 330B′, 330B″ is structured to be,and is, operatively coupled to a respective forming assembly 16, such aspreviously discussed in regard to FIGS. 2-6 . Thus, in an embodimentwith a single barrel cam 330B and two forming assemblies 16, such asshown in FIGS. 10 and 11 , the bodymaker 10B produces two can bodies percycle. Although only two forming assemblies 16 are shown in FIGS. 10 and11 being used in conjunction with barrel cam 330B, it is to beappreciated that more than two forming assemblies may be employedwithout varying from the scope of the present concepts. For example,additional forming assemblies 16 may be provided with the respective camfollower assemblies 150 thereof positioned to engage the 338B atgenerally any point around the barrel cam 330B (i.e., in addition to, orinstead of only at the top as shown in FIGS. 10 and 11 ). As an example,when viewed generally along the prime axis of rotation 333B of barrelcam 330B, an arrangement utilizing twelve forming assemblies 150 spacedequally about the circumference of the barrel cam 330B would generallyresemble the positioning of the twelve-hour indicators on the face of atraditional clock.

As described above, each forming assembly 16 is coupled, directlycoupled, or fixed to the mounting assembly 14. Thus, each formingassembly 16 is disposed at a fixed location adjacent the cam body 332.Further, relative to each forming assembly 16, the cam body ridge 338moves radially outwardly and radially inwardly as the cam body 332rotates. It is understood that as the radius of the cam body ridge 338decreases, the first cam surface 340 operatively engages a first camfollower member 156. Conversely, when as the radius of the cam bodyridge 338 increases, the second cam surface 342 operatively engages asecond cam follower member 158. It is understood that as one cam surface340, 342 operatively engages a cam follower member 156, 158, the othercam surface 340, 342 does not operatively engage a cam follower member156, 158. That is, only one cam surface 340, 342 operatively engages acam follower member 156, 158 at a time.

As the cam follower assembly 150 is coupled, directly coupled, or fixedto the forming assembly moving assembly ram assembly 120, the cam 330 isstructured to, and does, pull the ram body 122 radially inwardly as thefirst cam surface 334 operatively engages a first cam follower member156. Conversely, the cam 330 is structured to, and does, push the rambody 122 radially outwardly as the second cam surface 336 operativelyengages a second cam follower member 158. That is, as used herein, a camsurface/cam profile is a cam surface that “operatively engages” a camfollower, or constructs coupled to a cam follower, when the cam followermoves relative to the cam surface/cam profile and/or when the camsurface/cam profile moves relative to the cam follower.

As shown in FIG. 12 , the cooperative cam surfaces 334, 336, i.e., firstcam surface 334 and second cam surface 336, are divided into “portions.”That is, the cam surfaces 334, 336 include, or define, a number of driveportions 350, 352 (two shown). As used herein, a “drive” portion of acam surface means that the cam surface is structured to move anotherelement or assembly. In an exemplary embodiment, the cam surface driveportions 350, 352 include a forward or forming stroke portion 350 and arearward or return stroke portion 352. That is, as used herein, a“forward stroke” portion 350 is an alternate name for a drive portionthat causes a cam follower 150 (as well as constructs coupled to the camfollower 150 such as, but not limited to, the ram body 122) to movetoward an associated domer 58. Further, as used herein, a “rearwardstroke” portion 352 is an alternate name for a drive portion that causesa cam follower 150 (or constructs coupled to the cam follower 150 suchas, but not limited to, the ram body 122) to move away from anassociated domer 58.

As described above, the operative engagement of the second cam surface336 with the second cam follower member 158 causes the moving assembly44 of the forming assembly 16, including the ram body 122, to moveradially outwardly. Thus, a portion of the second cam surface 336wherein the radius is “increasing” as the cam body 332 moves is acooperative cam surface forward stroke portion 350. Conversely, theoperative engagement of the first cam surface 334 with the first camfollower member 156 causes the moving assembly 44 of the formingassembly 16, including the ram body 122, to move radially inwardly.Thus, a portion of the first cam surface 340 wherein the radius is“decreasing” as the cam body 332 moves is a cooperative cam surfacerearward stroke portion 352. As noted above, only one of first camsurface 334 or second cam surface 336 operatively engages a cam followermember 156, 158 at a time. As used herein, however, the opposed camsurfaces 334, 336 are identified by the same portion name. That is, theportion of the first cam surface 334 opposed to the second cam surfaceforward stroke portion 350 is also identified as the “forward strokeportion 350” even though the first cam surface 334 does not operativelyengage the first cam follower member 156 at the forward stroke portion350. Stated alternately, and further to the definition above, i.e., asused herein, a “forward stroke portion” 350 of associated first camsurface 334 and second cam surface 336, means a portion of thecooperative cam surfaces 334, 336 wherein at least one of thecooperative cam surfaces 334, 336 operatively engages, directly orindirectly, a ram body 122 and causes that ram body 122 to move towardan associated domer 58. Conversely, and further to the definition above,i.e., as used herein, a “rearward stroke portion” 352 of associatedcooperative first cam surface 334 and second cam surface 336 means aportion of the cooperative cam surfaces 334, 336 wherein at least one ofthe cooperative cam surfaces 334, 336 operatively engages, directly orindirectly, a ram body 122 and causes that ram body 122 to move awayfrom an associated domer 58.

Further, it is understood that as the cam body 332 rotates, thecooperative cam surface drive portions 350, 352 operatively engage a camfollower member 156, 158. Thus, each cooperative cam surface driveportion 350, 352 (or alternatively the cam body cooperative cam surfaceforward stroke portion 350 and the cam body cooperative cam surfacerearward stroke portion 352) has a beginning/upstream, first end 350U,352U and an ending/downstream, second end 350D, 352D. That is, as thecam body 332 rotates, the cooperative cam surface drive portion firstend 350U, 352U initially operatively engages a cam follower member 156,158. As the cam body 332 rotates further, the cooperative cam surfacedrive portion second end 350D, 352D passes by a cam follower member 156,158. When this occurs, the cam follower member 156, 158 is no longerdisposed at that cooperative cam surface drive portion 350, 352.

The nomenclature of [reference number]U and [reference number]D shall beused herein with each cam surface portion to identify the upstream,first end and downstream, second end of the named portion. For example,as discussed below, the cooperative cam surfaces 334, 336 also include,or define, a first dwell portion 360′. Thus, the upstream/first end ofthe first dwell portion 360′ is identified as “first dwell portion firstend 360′U.”

It is noted that the pitch (radial change relative to circumferentialchange) of the cam body ridge 338, and therefore the cooperative firstcam surface 334 and second cam surface 336, determines whether the camfollower member 156, 158, and therefore the ram body 122, moves at agenerally, or substantially, constant velocity, isaccelerating/decelerating (and/or the rate ofacceleration/deceleration), or is substantially stationary. That is, asa simplified example (exemplary elements not shown), it is assumed thata ram must move forward (toward a domer) three inches. Further, it isassumed that the cam body cooperative cam surface forward stroke portionextends over an arc of ninety degrees (90°). For this exemplaryconfiguration, the radius of the cooperative cam surfaces and morespecifically the second cam surface, increases three inches over theninety degrees (90°) of the cam body cooperative cam surface forwardstroke portion. That is, the movement of the ram body is proportional tothe radius of the cooperative cam surfaces. Thus, when the radius of thecooperative cam surfaces increases an inch, the ram moves forward aninch.

Further, as noted and in an exemplary embodiment, the cooperative camsurface drive portion 350 (or alternatively the cam body cooperative camsurface forward stroke portion 350) have a substantially constantvelocity cam profile, i.e., a shape structured to impart a substantiallyconstant velocity to the element/assembly that is operatively engaged bythe cam surface. In the example above (exemplary elements not shown),wherein the radius of the cooperative cam surfaces and more specificallythe second cam surface, increases three inches over the ninety degrees(90°), an increase in the radius of one inch every 30° would produce asubstantially constant velocity in the ram.

A cam body ridge 338, and therefore the cooperative first cam surface334 and second cam surface 336, which operatively engages a cam follower(or constructs coupled to the cam follower such as, but not limited to,the ram body 122) and which has a pitch that is structured to, and does,produce a substantially constant velocity in the cam follower (orconstructs coupled thereto) has, as used herein, a “substantiallyconstant velocity cam profile.” In an exemplary embodiment, at least oneof, or both, the cooperative cam surface forward stroke portion 350 andthe cooperative cam surface rearward stroke portion 352 have asubstantially constant velocity cam profile. Further, in an exemplaryembodiment, the cooperative cam surface forward stroke portion 350extends over an arc of about one hundred eighty-three and one-halfdegrees (183.5°) and the cooperative cam surface rearward stroke portion352 extends over an arc of about one hundred and forty-three degrees(143.0°).

In an exemplary embodiment, the cooperative cam surfaces 334, 336 alsoinclude, or define, a number of dwell portions 360′, 360″ (two shown)and identified herein as the first dwell portion 360′ and the seconddwell portion 360″. As used herein, a “dwell portion” 360′, 360″ of theassociated cooperative first cam surface 334 and second cam surface 336,means a portion of the cooperative cam surfaces 334, 336 wherein neitherof the cooperative cam surfaces 334, 336 operatively engages a camfollower (or constructs coupled to the cam follower such as, but notlimited to, the ram body 122). Thus, the ram body 122 is generallystationary and does not move toward or away from an associated domer 58.In an exemplary embodiment, and at a cooperative cam surface dwellportion 360′, 360″, the radius of the cam body ridge 338, and thereforethe cooperative first cam surface 334 and second cam surface 336, doesnot substantially increase or decrease. Thus, the cam body ridge 338,and therefore the cooperative first cam surface 334 and second camsurface 336, do not operatively engage a cam follower member 154 (orconstructs coupled to the cam follower member 154 such as, but notlimited to, the ram body 122). As used herein, a cam surface that doesnot operatively engage a cam follower member 154 has a “no velocity camprofile.” That is, a “no velocity cam profile” means that cooperativecam surfaces 334, 336 do not cause a cam follower (or constructs coupledto the cam follower such as, but not limited to, the ram body 122) tomove toward or away from an associated domer 58. Thus, the cooperativecam surface dwell portions 360′, 360″ have a “no velocity cam profile.”However, to maintain consistent terminology, hereinafter the first dwellportion 360′ and the second dwell portion 360″ will be said to “engage”or “operatively engage” the moving assembly 44 of a forming assembly 16(or elements thereof such as, but not limited to, the cam followermembers 154). It is understood that while the terms “engage” or“operatively engage” are used, the first dwell portion 360′ and thesecond dwell portion 360″ do not actually cause the moving assembly 44(or elements thereof such as, but not limited to, the cam followermembers 154) to move. That is, with respect to the first dwell portion360′ and the second dwell portion 360″ only, and as used herein, theterms “engage” and “operatively engage” do not have the meanings setforth above and instead mean that the first dwell portion 360′ and thesecond dwell portion 360″ are directly coupled to the cam followerassembly 150.

In an exemplary embodiment, no cooperative cam surface dwell portion360′, 360″ extends over an arc greater than thirty degrees (30°). Asused herein, the existence of cooperative cam surface dwell portions360′, 360″ extending over an arc no greater than thirty degrees does notmean that the cam body ridge 338 has a generally, or substantially,consistent radius relative to the cam body 332 axis of rotation. Thatis, so long as the cooperative cam surface dwell portions 360′, 360″extend over an arc no greater than thirty degrees, the cam body ridge338 does not have a generally, or substantially, consistent radiusrelative to the cam body 332 axis of rotation.

In an exemplary embodiment, at least one cam body cooperative camsurface dwell portion 360′, 360″ is disposed between at least one of thecam body cooperative cam surface forward stroke portion 350 and the cambody cooperative cam surface rearward stroke portion 352, or, the cambody cooperative cam surface rearward stroke portion 352 and the cambody cooperative cam surface forward stroke portion 350. In anotherexemplary embodiment, each cooperative cam surface dwell portion 360′,360″ is disposed between cam body cooperative cam surface drive portions350, 352. That is, there is a cooperative cam surface first dwellportion 360′ disposed between the forward stroke portion second end 350Dand the rearward stroke portion first end 352U, and, a cooperative camsurface second dwell portion 360″ disposed between the rearward strokeportion second end 352D and the forward stroke portion first end 350U.In an exemplary embodiment, the cooperative cam surface first dwellportion 360′ extends over an arc of about three-and one-half degrees(3.5°) and the cooperative cam surface second dwell portion 360″ extendsover an arc of about thirty degrees (30°).

In an exemplary embodiment, the cooperative cam surfaces 334, 336 alsoinclude, or define, a number of portions 370, 372 (two shown),hereinafter identified as the acceleration portion 370 and thedeceleration portion 372. The acceleration portion 370 and thedeceleration portion 372 each have an “acceleration profile.” As usedherein, an “acceleration profile” means that the cam body ridge 338, andtherefore the cooperative first cam surface 334 and second cam surface336, operatively engages a cam follower (or constructs coupled to thecam follower such as, but not limited to, the ram body 122) and producea changing velocity in a ram body 122. That is, an “accelerationprofile” means that the cam body ridge 338, and therefore thecooperative first cam surface 334 and second cam surface 336 has/have apitch that is structured to, and does, produce a changing velocity in acam follower (or constructs coupled to the cam follower such as, but notlimited to, the ram body 122) when the cam surface operatively engagesthe cam follower. Thus, the surface portions 370, 372 either cause a rambody 122 to increase or decrease its velocity. That is, deceleration ofa ram body's 122 velocity is, stated alternately, acceleration in adirection opposite the velocity of the ram body 122.

In an exemplary embodiment such as illustrated in FIG. 12 , thecooperative cam surface acceleration portion 370 and decelerationportion 372 are disposed between the cooperative cam surface driveportions 350, 352 and the cooperative cam surface dwell portions 360′,360″. That is, starting at the end of dwell portion 360″ associated withthe ram body 122 being in the first position (i.e., furthest from thedomer 58), and moving sequentially about the cam surfaces 334, 336, theportions are in this order: the acceleration portion 370 (which causesan acceleration of the ram body 122 toward the domer 58), a constantspeed portion 350, the deceleration portion 372 (which causes adeceleration to no velocity), the first dwell portion 360′, the varyingspeed portion 352 which is of varying speed, and the second dwellportion 360″. The acceleration portion 370, the constant speed portion350, and the deceleration portion 372 make up the forming stroke,whereas the varying speed portion 352 makes up the return stroke. In anexemplary embodiment such as shown in FIG. 12 , the acceleration portion370 extends over an arc of about thirty-three degrees (33°) and thedeceleration portion 372 extends over an arc of about thirty-three andone-half degrees (33.5°).

Thus, as shown in FIG. 12 , and in an exemplary embodiment, thecooperative first cam surface 334 and second cam surface 336, aredivided into the following portions which extend sequentially over theidentified arcs.

Acceleration portion 370 0° to 33° Constant speed portion 350 33° to150° Deceleration portion 372 150° to 183.5° First dwell portion 360′183.5° to 187° Varying speed portion 352 187° to 330° Second dwellportion 360″ 330° to 360°

For a cam 330 such as described above, FIG. 12A shows the position ordisplacement of a punch 124 relative to the first position and relativeto the cam 330, as described above, as the cam 330 rotates. FIG. 12Bshows the velocity of a ram assembly 120/punch 124 as the cam 330rotates. FIG. 12C shows the acceleration (or deceleration) of a ramassembly 120/punch 124 as the cam 330 rotates.

When a forming assembly 16 is coupled, directly coupled, or fixed to themounting assembly 14, the cam body ridge 338 is disposed between thefirst cam follower member 156 and the second cam follower member 158.That is, as noted above, the wheel 186 of the first cam follower member156 is disposed adjacent to the first cam surface 334, and, the wheel186 of the second cam follower member 158 is disposed adjacent to thesecond cam surface 336. Thus, when the cam 330, i.e., cam body 332,rotates, and when the radius of the cam body ridge 338 is “decreasing”as described above, the first cam surface 334 operatively engages thefirst cam follower member 156. Conversely, when the cam 330, i.e., cambody 332, rotates, and when the radius of the cam body ridge 338 is“increasing” as described above, the second cam surface 336 operativelyengages the second cam follower member 158.

The operative engagement of the first and second cam follower members156, 158 by the cooperative cam surfaces 334, 336 cause the cam followerassembly 150 and the elements coupled thereto, i.e., the ram assembly120, to move. That is, the operative engagement of the first and secondcam follower members 156, 158 by the cooperative cam surfaces 334, 336cause the moving assembly 44 of the forming assembly 16 to move.

Thus, the motion of the moving assembly 44 of a forming assembly 16sequentially occurs as follows. Initially, the moving assembly 44 is inthe first position. When the first and second cam follower members 156,158 are at the second dwell portion 360″, the moving assembly 44(including the ram body 122 and the punch 124) does/do not move. As themoving elements of the moving assembly 44 do not suddenly, or instantly,reverse directions, the moving assembly 44 does not substantiallyvibrate. This solves the problem(s) noted above. That is, the secondcooperative cam surface dwell portion 360″ solves the problem(s) notedabove. Further, at this time, a cup is moved into position at the mouthof the die pack 56.

As the cam 330, i.e., cam body 332, rotates, the first cooperative camsurface acceleration portion 370 engages the first and second camfollower members 156, 158 which causes the moving assembly 44 (includingthe ram body 122 and the punch 124) to accelerate and move toward theassociated domer 58. As the cam 330, i.e., cam body 332, continues torotate, the cooperative cam surface forward stroke portion 350 engagesthe first and second cam follower members 156, 158 which causes themoving assembly 44 (including the ram body 122 and the punch 124) tomove toward the associated domer 58 at a substantially constantvelocity. This solves the problem(s) noted above. That is, thecooperative cam surface forward stroke portion 350 solves the problem(s)noted above.

As the cam 330, i.e., cam body 332, continues to rotate, thedeceleration portion 372 engages the first and second cam followermembers 156, 158 which causes the moving assembly 44 (including the rambody 122 and the punch 124) to decelerate, i.e., accelerate in adirection opposite the velocity, to no velocity. As the cam 330, i.e.,cam body 332, continues to rotate, the first cooperative cam surfacedwell portion 360′ engages the first and second cam follower members156, 158 which causes the moving assembly 44 (including the ram body 122and the punch 124) to be maintained in the second position. That is, asthe moving elements of the moving assembly 44 do not suddenly, orinstantly, reverse directions, the moving assembly 44 does notsubstantially vibrate. The lack of motion/acceleration when the movingassembly 44 is in the second position solves the problem(s) noted above.That is, the first cooperative cam surface dwell portion 360′ solves theproblem(s) noted above.

Moreover, because the moving assembly 44 dwells in the second position(and in the first position, as discussed below) prior to reversing thedirection of the motion, the moving assembly 44 is not subject to“whiplash.” This, in turn, means that the elements of the movingassembly 44 are not subject to elongation as described above. Statedalternately, and as used herein, a ram drive assembly 300 that isstructured to, and does, avoid “whiplash” in any element operativelyengaged thereby is a “steady state” drive assembly. Similarly, a cam330, or a cam body 332, that is structured to, and does, avoid“whiplash” in any element that is operatively engaged by the cam 330, ora cam body 332, is a “steady state” cam 330, or cam body 332. Thissolves the problem(s) noted above.

As the cam 330, i.e., cam body 332, continues to rotate, the cooperativecam surface rearward stroke portion 352 engages the first and second camfollower members 156, 158 which causes the moving assembly 44 (includingthe ram body 122 and the punch 124) to move with a motion generally lowin acceleration, pressure angle, and vibrations. This solves theproblem(s) noted above. That is, the cooperative cam surface rearwardstroke portion 352 solves the problem(s) noted above.

As the cam 330, i.e., cam body 332, continues to rotate, the secondcooperative cam surface dwell portion 360″ again engages the first andsecond cam follower members 156, 158 as the cycle begins again. It isunderstood that each time the cam body 322 rotates 360 degrees, i.e.,and as used herein, one “cycle” of the bodymaker 10, a forming assembly16 makes a can body.

As noted above in conjunction with FIG. 5 , one cam follower mountingpassage 175 includes an eccentric bushing 187 with the orientation tab194. The eccentric bushing 187 is structured to, and does, allow the camfollower assembly 150 to move between two configurations. That is, whenthe eccentric bushing 187 is disposed so that the thinner side 188″ isdisposed closer to the mounting assembly body passage 20, the distancebetween the cam follower members 154 is at a maximum. This is the firstconfiguration of the cam follower assembly 150. In this configuration,the distance between the cam follower members 154 is greater than theradial width W of the cam body ridge 338. Thus, as described below, theforming assembly 16 is able to be moved in a direction generally normalto the plane of the cam body 332 without contacting the cam body ridge338. That is, when the cam body 332 is disposed so that the plane of thecam body 332 is generally horizontal, and when the cam follower assembly150 is in the first configuration, the forming assembly 16 is able to belifted, or lowered (e.g., via a suitable overhead lift mechanism),relative to the cam body 332 without the cam follower assembly 150contacting, or substantially contacting, the cam body ridge 338. It isunderstood that when the forming assembly moving assembly cam followerassembly 150 is in the first configuration, the cam follower rollerbearing eccentric bushing orientation tab 194 is fixed via any suitablearrangement (e.g., a radial recess). Thus, the eccentric bushing 187 isnot able to rotate within the mounting passage 175.

Conversely, when the eccentric bushing 187 is disposed so that thethicker side 188″ is disposed closer to the mounting assembly bodypassage 20 (such as shown in FIG. 5 ), the distance between the camfollower members 154 is at a minimum. This is the second configurationof the forming assembly moving assembly cam follower assembly 150. Inthis configuration, the distance between the cam follower members 154 isgenerally, or substantially, the same as the radial width W of the cambody ridge 338. This is the operational configuration of the camfollower assembly 150. In this configuration, any radial change in theposition of the cam body ridge 338, i.e., the associated cooperative camsurfaces 334, 336, or, first cam surface 340 and second cam surface 342,causes the cooperative cam surfaces 334, 336 to operatively engage thecam follower assembly 150.

In this configuration, the bodymaker 10 solves the problem(s) statedabove. That is, for example, the ram drive assembly 300 is a “direct”ram drive assembly 300, as that term is defined above. That is, the ramdrive assembly 300 is structured to, and does, convert a rotationalmotion (from the motor output shaft 312) to a reciprocal motion (of theram body 122) without a pivoting construct such as, but not limited to,a swing arm. This solves the problem(s) noted above.

It is further noted that a bodymaker 10 as described above with a diskcam 330 has a configuration unlike known bodymakers. As noted above,each ram body 122 has a longitudinal axis L. Further, the cam body 332axis of rotation is a “prime axis of rotation” for the bodymaker ramdrive assembly 300, as that term is defined above. Thus, the cam body332 axis of rotation is also identified herein as the “ram driveassembly prime axis of rotation 333.” As described above, each ram bodylongitudinal axis L extends generally radially relative to the ram driveassembly prime axis of rotation 333 (e.g., see FIG. 2 ). That is, theram body longitudinal axes L are generally disposed in a plane and areradially offset about the ram drive assembly prime axis of rotation 333.In an exemplary embodiment, the forming assemblies 16 are generallyevenly disposed about the ram drive assembly prime axis of rotation 333.That is, for “N” number of forming assemblies 16, the forming assemblies16 are disposed about 360°/N degrees apart. In an exemplary embodiment,there are two or more forming assemblies 16 disposed about the ram driveassembly prime axis of rotation 333. That is, in an exemplaryembodiment, the number of forming assemblies 16 includes between two andten forming assemblies 16. Further, in an exemplary embodiment, thenumber of forming assemblies 16 includes one of two forming assemblies16, four forming assemblies 16, six forming assemblies 16, eight formingassemblies 16 or ten forming assemblies 16.

Further, in an exemplary embodiment, when there is an even number offorming assemblies 16, each forming assembly 16 may be disposedgenerally in opposition to another forming assembly 16 across the ramdrive assembly prime axis of rotation 333 (i.e., positioned generally180° about the prime axis 333). However, it is to be appreciated thatthe drive arrangements as described herein allow for the formingassemblies 16 to be positioned in other configurations that are not inopposition to each other across the ram drive assembly prime axis ofrotation 333 (i.e., positioned other than 180° with respect to eachother). For example, in one exemplary embodiment, a bodymaker 10includes only two forming assemblies 16 positioned only 45° apart aboutthe prime axis 333. In another example, a bodymaker 10 includes only twoforming assemblies 16 positioned only 36° apart about the prime axis333. Further, it is to be appreciated that the angular spacing betweenadjacent forming assemblies 16 of a bodymaker 10 may differ among pairsof forming assemblies 16 within the bodymaker 10. As an example, withoutlimitation, a bodymaker 10 having three forming assemblies 16 may havetwo of the forming assemblies 16 positioned 90° apart about the primeaxis 333, with the third forming assembly spaced 135° about the primeaxis 333 relative to each of the other two forming assemblies 16. In anyof these configurations, the ram drive assembly 300 is a “singlesource/[X]-output ram drive assembly,” as that term is defined above.That is, for example, if the forming system 12 includes three formingassemblies 16, the ram drive assembly 300 is a single source/3-outputram drive assembly. Thus, for a forming system 12 including one of four,five, six, seven, eight, nine or ten forming assemblies 16, the ramdrive assembly 300 is a single source/4-output ram drive assembly, asingle source/5-output ram drive assembly, a single source/6-output ramdrive assembly, a single source/7-output ram drive assembly, a singlesource/8-output ram drive assembly, a single source/9-output ram driveassembly, a single source/10-output ram drive assembly, respectively. Anembodiment with eight forming assemblies 16 is shown in FIG. 13 .

In an exemplary embodiment, the forming system 12 includes four formingassemblies 16. As shown in FIG. 2 , the four forming assemblies 16 aredisposed about, or substantially, ninety degrees apart about the primeaxis 333 of the ram drive assembly 300. Further, in this configuration,the forming assemblies 16 are “asymmetrical forming assemblies.” Thatis, in this configuration, the forming elements do not movesubstantially in opposition to each other.

In an embodiment such as shown in FIG. 11 wherein the bodymaker is abarrel cam 330B, the axis of rotation of the cam body 332B defines aprime axis of rotation 333B. In this embodiment, however, thelongitudinal axis L of each ram body 122 extends generally parallel tothe prime axis of rotation 333B of the barrel cam 330B.

Another aspect of the motion of the ram assembly 120, i.e., the ram body122, caused by operative engagement by a cam 330 of a ram drive assembly300 as described above is that no two ram bodies are in the same “medialposition” at one time. That is, for example, no two ram bodies 122 aredisposed with the punch 124 entering the die pack 56 associatedtherewith at the same time. It is noted, however, that two ram bodies122 are, in certain configurations, disposed with the punch 124 in diepack 56 associated therewith at the same time. That is, for example, theforming system 12 with the cam 330 in a specific orientation may haveone ram body 122 with the punch 124 at the upstream end of the die pack56 associated therewith while another ram body 122 has the punch 124disposed at the downstream end of the die pack 56 associated therewith.When the forming assemblies 16 are “asymmetrical forming assemblies,”the power needed, i.e., the size/power of the motor 310 is reducedbecause no ram assemblies 120 are disposed at the same time in alocation that generates the maximum resistance. This solves theproblem(s) noted above. Further, the bodymaker 10, i.e., the ram driveassembly 300, as described above is structured to, and selectively does,operate with less than the full set of forming assemblies. That is, thebodymaker 10 as described above has a number of forming assemblies 16.Whatever the maximum number of forming assemblies 16 associated with aspecific bodymaker 10 is, as used herein, a “full set” of formingassemblies 16. For example, in an embodiment wherein the maximum numberof forming assemblies 16 is four, the “full set” of forming assemblies16 means four forming assemblies 16.

Unlike prior art bodymakers which needed to balance the loads created bythe forming assemblies 16, the present bodymaker 10 is structured to,and, when required, does, operate with less than a “full set” of formingassemblies 16. For example, in an embodiment wherein the “full set” offorming assemblies 16 means four forming assemblies 16, the bodymaker10, i.e., the ram drive assembly 300, is structured to, and does,operate with three, two, or one forming assemblies 16. This solves theproblem(s) noted above.

Stated alternately, the bodymaker 10 is structured to, and when requireddoes, operate with fewer than all forming assemblies operatively coupledto the drive assembly. That is, unlike a prior art bodymaker having twoforming assemblies coupled to a crank, the use of a cam 330 eliminatesthe need for the drive assembly to be balanced. Thus, for example, ifone of four forming assemblies 16 needs repaired, the defective formingassembly 16 is disengaged from the drive assembly 300 and then theremaining three forming assemblies 16 are put back into operation. Asused herein, a bodymaker drive assembly 300 that is structured tooperate with less than all forming assemblies 16 engaged thereby is a“limited load” drive assembly 300. Use of a limited load drive assembly300 solves the problem(s) noted above.

In an exemplary embodiment, such as shown in FIGS. 3, 4 and 6 , themounting assembly 14 further includes a number of forming assemblypositioning assemblies 400. There is one positioning assembly 400associated with each forming assembly 16. When the mounting assemblybody 18 is disposed in a generally horizontal plane, each positioningassembly 400 is substantially disposed below the mounting assembly body18. Each forming assembly positioning assembly 400 is structured to, anddoes, move (and in this configuration lift/lower) a forming assembly 16.That is, each forming assembly positioning assembly 400 is structuredto, and does, move a forming assembly 16 among a first (non-operational)position, such as shown in FIG. 6 , wherein the forming assembly 16 isspaced from an associated mounting assembly planar body upper surfacerecess 34 (i.e., is above an associated mounting assembly planar bodyupper surface recess 34), and a second (operational) position such asshown in FIG. 4 , wherein the forming assembly 16 is disposed within anassociated mounting assembly planar body upper surface recess 34.

In the illustrated exemplary embodiment, each positioning assembly 400includes a fluid pressure source 402 and a number of actuators 404coupled thereto via fluid conduits 406. The fluid pressure source 402may be any suitable source of pneumatic or hydraulic pressure (e.g.,without limitation an air compressor, an hydraulic pump, a supply linefrom a remote pressure source, etc.). Each actuator may be a suitablepneumatic or hydraulic actuator coupled to the corresponding suitablepressure source via flexible or rigid conduits 406. Control of movementof each actuator 404 may be provided via any suitable controlarrangement (not numbered). Alternatively, each positioning assembly mayutilize electric actuators powered by a suitable source of electricalpower and controlled by a suitable controller. Additionally, eachpositioning assembly 400 may include one or more suitable lockingmechanisms (not numbered, e mechanical and/or electromagneticarrangements) for securing each forming assembly 16 to mounting assembly14.

It is to be understood that, when a forming assembly 16 is being movedbetween the first and second positions, and when the forming assembly 16is in the first (non-operational) position, the cam follower assembly150 is in the first (widely spaced) configuration previously discussed.Further, when the forming assembly 16 is in the second (operational)position, the cam follower assembly 150 is in the second (closelyspaced) configuration previously discussed.

When the mounting assembly planar body upper surface recesses 34 are“machined” recesses 34, each forming assembly 16 is automaticallypositioned as the forming assembly 16 is moved into the machinedmounting assembly planar body upper surface recess 34. Alternatively,after a forming assembly 16 is disposed in a mounting assembly planarbody upper surface recess 34, a user brings the forming assembly 16 intothe proper alignment by passing guide pins 39 through the associatedguide pin passages 36, 68. Further, a guide pin 39 is temporarilydisposed in the alignment pin passage 178 of the slider 152 of the camfollower assembly 150 and the alignment passage 344 of the cam 330. Useof the guide pins 39 brings each forming assembly 16 into properalignment with the cam 330. It is again noted that each forming assembly16 is, in an exemplary embodiment, an aligned, unitary forming assembly16; thus, the elements with each forming assembly 16 do not requirefurther alignment. This solves the problem(s) noted above.

In one embodiment, the bodymaker 10 includes a single forming assembly16. In another embodiment, the bodymaker 10 includes a plurality offorming assemblies 16. In another embodiment, the bodymaker 10 includesan even number of forming assemblies 16. Thus, in an exemplaryembodiment, the number of forming assemblies includes one of a singleforming assembly 16, two forming assemblies 16, four forming assemblies16, six forming assemblies 16, eight forming assemblies 16 or tenforming assemblies 16. Further, and as described above, with formingassemblies 16 disposed about the cam body 332 axis of rotation, thelongitudinal axes of the forming assemblies 16 extend generally, orsubstantially, radially relative to the cam 320 axis of rotation.

Further, in a configuration disclosed above wherein the bodymaker 10includes more than two forming assemblies 16, the bodymaker 10 producesmore than two can bodies per cycle. This solves the problem(s) notedabove. That is, for example, in an embodiment with four formingassemblies 16, the bodymaker 10 produces four can bodies per cycle.Moreover, with a cam 330 rotating at 320 r.p.m., the bodymaker 10 withfour forming assemblies 16, or alternately, the forming system 12 withfour forming assemblies 16, produces one of a large number of can bodiesper minute, a very large number of can bodies per minute, or anexceedingly large number of can bodies per minute. As used herein, a“large” number of can bodies per minute means more than 1,280 can bodiesper minute. As used herein, a “very large” number of can bodies perminute means more than 1,440 can bodies per minute. As used herein, an“exceedingly large” number of can bodies per minute means more than1,600 can bodies per minute. A bodymaker 10 that produces any of a largenumber of can bodies per minute, a very large number of can bodies perminute, or an exceedingly large number of can bodies per minute solvesthe problem(s) noted above.

Further, the can bodymaker 10 as described above occupies a “reduced”floor space as compared to conventional bodymakers. As used herein, theterm “floor space” includes the space bound by the perimeter of theelements extending from the bodymaker. For example, FIG. 13 shows anoverhead view of a layout of a bodymaker 10′ in accordance with anexemplary embodiment of the disclosed concept having eight formingassemblies 16 and related machinery (e.g., trimmers). Such layoutoccupies/requires a floor space having dimensions of about D1′×D2′. Insuch example both D1′ and D2′ are 366 inches. Hence, the overall floorspace occupied/required by such layout is 133,956 in² or about 930 ft².In comparison, FIG. 14 shows a layout of eight prior art bodymakers 1(i.e., the number of prior art bodymakers 1 needed to achieve the sameor similar output as bodymaker 10′ of FIG. 13 ) and related machinery.Such layout occupies/requires a floor space having dimensions of aboutD1×D2. In such example D1 is 885.5 inches and D2 is 432 inches. Hence,the overall floor space occupied/required by such layout is 382,536 in²or about 2,656 ft², almost three times the floor space as the bodymaker10′ in accordance with the disclosed concept. As a bodymaker inaccordance with the disclosed concept provides for similar output whilerequiring a lesser or “reduced” floor space such bodymaker occupies a“reduced” floor space as compared to conventional bodymakers.

In addition to saving floor space, it is to be appreciated thatbodymakers in accordance with the disclosed concept require less energyto produce an equivalent amount of can bodies as compared toconventional arrangements. As an example, a conventional single headbodymaker requires a 75 HP motor. A recently released two head unit alsorequires 75 HP, and a four head unit requires 300 HP. In stark contrast,a four head (i.e., four forming assembly 16) bodymaker in accordancewith the disclosed concept requires only a single 30 HP motor. Hence forthe same can body output, a bodymaker in accordance with the disclosedconcept provides significant energy savings. Further, conventionalbodymakers require flywheels of considerable mass to supply the energyneeded to form a can due to their forming/drive arrangement(s). Incontrast, bodymakers in accordance with the disclosed concept do notrequire such flywheels because of the low mass of the forming assemblyas well as the profile available due to the use of the disk cam (i.e.,zero acceleration portions at the end of the strokes and, consequently,zero inertia forces and deformations).

While specific embodiments of the invention have been described indetail, it will be appreciated by those skilled in the art that variousmodifications and alternatives to those details could be developed inlight of the overall teachings of the disclosure. Accordingly, theparticular arrangements disclosed are meant to be illustrative only andnot limiting as to the scope of invention which is to be given the fullbreadth of the claims appended and any and all equivalents thereof.

What is claimed is:
 1. A can bodymaker comprising: a ram drive assemblyincluding a disk cam; and a moving assembly comprising: a ram assemblyincluding an elongated ram body having a proximal end and an oppositedistal end; and a cam follower assembly coupled to the proximal end ofthe ram body, the cam follower assembly comprising: a slider; and aplurality of cam follower members rotatably coupled to the slider,wherein the cam follower members are operatively engaged with the diskcam.
 2. The can bodymaker of claim 1, wherein the cam follower assemblyfurther comprises a cam follower bearing assembly having a number ofhydrostatic/hydrodynamic bearing pads positioned and structured toengage with corresponding, cooperatively positioned, bearing members. 3.The can bodymaker of claim 2, wherein each bearing pad includes arecessed bearing pocket that is structured to house a pressurized supplyof bearing fluid provided therein.
 4. The can bodymaker of claim 2,wherein the slider comprises a slider body and an upper frame portionextending upward from the slider body, and wherein the number ofhydrostatic/hydrodynamic bearing pads are provided on the upper frameportion.
 5. The can bodymaker of claim 4, wherein the upper frameportion of the slider body comprises: a first member extending upwardfrom at or about a first edge of the slider body; a second memberextending upward from at or about a second edge of the slider body; anda third member extending between the first and second members and spaceda distance above the slider body.
 6. The can bodymaker of claim 5,wherein the number of hydrostatic/hydrodynamic bearing pads includes: afirst bearing pad coupled to an outward facing face of the first member;a second bearing pad coupled to an outward facing face of the secondmember; and a third bearing pad coupled to an upward facing face of thethird member.
 7. The can bodymaker of claim 4, wherein the sliderfurther comprises a lower frame portion extending downward from theslider body.
 8. The can bodymaker of claim 7, wherein the lower frameportion comprises: a first member extending downward from at or about afirst edge of the slider body; a second member extending downwardgenerally from at or about a second edge of the slider body opposite thefirst edge; and a third member extending between the first and secondmembers and spaced a distance below the slider body.
 9. The canbodymaker of claim 1, wherein each of the cam followers comprises aroller bearing.
 10. The can bodymaker of claim 9, wherein one of theroller bearings includes an eccentric bushing positionable between afirst positioning, wherein the one roller bearing is disposed the fixeddistance from the other roller bearing, and a second positioning,wherein the one roller bearing is disposed a fixed second distance,different than the fixed distance, from the other roller bearing.
 11. Acan bodymaker comprising: a ram drive assembly including one of a diskcam or a barrel cam; and a moving assembly comprising: a ram assemblyincluding an elongated ram body having a proximal end and an oppositedistal end; and a cam follower assembly coupled to the proximal end ofthe ram body, the cam follower assembly comprising: a slider; and aplurality of cam follower members rotatably coupled to the slider,wherein the cam follower members are operatively engaged with one of thedisk cam or the barrel cam, wherein each of the cam followers comprisesa roller bearing, and wherein one of the roller bearings includes aneccentric bushing positionable between a first positioning, wherein theone roller bearing is disposed a first distance from another one of theplurality of roller bearings, and a second positioning, wherein the oneroller bearing is disposed a second distance, different than the firstdistance, from the other one of the plurality of roller bearings. 12.The can bodymaker of claim 11, wherein the cam follower assembly furthercomprises a cam follower bearing assembly having a number ofhydrostatic/hydrodynamic bearing pads positioned and structured toengage with corresponding, cooperatively positioned, bearing members.13. The can bodymaker of claim 12, wherein each bearing pad includes arecessed bearing pocket that is structured to house a pressurized supplyof bearing fluid provided therein.
 14. The can bodymaker of claim 12,wherein the slider comprises a slider body and an upper frame portionextending upward from the slider body, and wherein the number ofhydrostatic/hydrodynamic bearing pads are provided on the upper frameportion.
 15. The can bodymaker of claim 14, wherein the upper frameportion of the slider body comprises: a first member extending upwardfrom at or about a first edge of the slider body; a second memberextending upward from at or about a second edge of the slider body; anda third member extending between the first and second members and spaceda distance above the slider body.
 16. The can bodymaker of claim 15,wherein the number of hydrostatic/hydrodynamic bearing pads includes: afirst bearing pad coupled to an outward facing face of the first member;a second bearing pad coupled to an outward facing face of the secondmember; and a third bearing pad coupled to an upward facing face of thethird member.
 17. The can bodymaker of claim 14, wherein the sliderfurther comprises a lower frame portion extending downward from theslider body.
 18. The can bodymaker of claim 17, wherein the lower frameportion comprises: a first member extending downward from at or about afirst edge of the slider body; a second member extending downwardgenerally from at or about a second edge of the slider body opposite thefirst edge; and a third member extending between the first and secondmembers and spaced a distance below the slider body.